KR20080048897A - Planetary gearboxes and vehicles using them - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear type transmission suitable for a bicycle, a wheelchair, or a similar vehicle, wherein two planetary gear trains are combined to integrate one carrier and the other internal gear, respectively, the input side and the output side. The two carriers, which are divided and operated together, form a housing of the transmission, install a double planetary gear or multiple planetary gears, and couple or separate each sun gear rotatably installed on a fixed central axis, The shifting is controlled by integrating or separating the two sun gears.

According to the present invention, the carrier serves as a housing of the transmission and is small and light, and the central shaft is detachable to the vehicle body, and provides a planetary gear type transmission in which acceleration, deceleration, and constant speed are smoothly shifted without using a clutch.

Description

Planetary gear transmission and vehicle using same

1 is a perspective view showing a mounting state of a wheelchair wheel to which an embodiment of the planetary gear transmission according to the present invention is applied.

        a) perspective view from the outside b) perspective view from the inside

FIG. 2 is an exploded perspective view illustrating the parts of the planetary gear transmission of FIG. 1

3 is a partial cross-sectional view of the planetary gearbox of FIG. 1.

4 is a cross-sectional view taken along the line A-A of FIG. 3 showing a state in which the sun gear 8 is fixed and accelerated.

FIG. 5 is a partial cross-sectional view showing a direct connection state of the planetary gear type transmission of FIG. 1 showing the state where the acceleration sun gear 8 and the reduction sun gear 9 are pressurized by the home cam 6 to be integrated.

FIG. 6 is a cross-sectional view taken along the line BB of FIG. 3 to show the state in which the sun gear 9 is fixed to decelerate one speed shift.

7 is a cross-sectional view taken along the line C-C of FIG.

8 is a perspective view of a shift sleeve according to the embodiment of FIG. 1;

9 is a perspective view of a home cam rotation direction fixing member according to the embodiment of FIG.

10 is a perspective view of a home cam according to the embodiment of FIG.

11 is a perspective view of a sun gear 8 having side projections according to the embodiment of FIG. 1.

12 is a perspective view of a sun gear 9 having side protrusions according to the embodiment of FIG. 1.

1: center axis 2: center axis pin

3: shifting sleeve 4: groove cam rotation direction fixing member

5: shift sleeve return spring 6: first home cam

7: Second Homecam 8: Accelerated Sun Gear

9: reduction gear 1 sun gear 10: acceleration planetary gear

11: Reduced gear 1 planetary gear 12: Ring gear with output carrier

13: ring gear with input carrier 14: input carrier

15: input carrier ring gear holder 16: input carrier push holder

17: output carrier (wheel center) 18: wheels

19, 20, 21: planetary gear shaft 22: reduction gear 2 planetary gear

23: reduction gear 2 sun gear

24: spring 25: shift shaft coupling ring

26: Old 27: Wheel central axis field bed

28: center shaft fixing member 29: disk hub

30: shifting strap 31: shifting strap

32: shifting line fixing screw 33: shifting line guide plate

35: shifting line

100: wheelchair (body) 110: caliper brake

111: disk hub 112: disk

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear transmission suitable for use in a bicycle, a wheelchair, or a similar vehicle. In particular, by combining two planetary gear trains, the carrier serves as the transmission housing and is small and light, and the central shaft is detachable from the vehicle body. The invention relates to a planetary gearbox that is capable of smoothly accelerating, decelerating and constant speed without using a clutch.

In general, the gearbox is a device for shifting the rotational speed of the rotating shaft, and the gearbox is used to change the rotational shaft by using a belt, a friction wheel, and a gear. Used external gear shifting, an internal gear in which one gear is interlocked in another gear, and a planetary gear shift in which a pinion gear is connected to the outer circumference of the sun gear are interlocked.

In particular, in the case of a gear configured using a spur gear and a helical gear, which are external gears, and a differential shield, the impact force due to the collision between the teeth of the gear and the teeth during the engagement of the gears for rotational shaft shifting acts on the teeth of each gear. , There is a problem that the gear teeth are worn out or damaged while the load is concentrated on the gear teeth during rotation due to the gearing between the gears. Particularly, since the gear teeth are partially engaged with each other when the gear teeth are engaged, the gear teeth are worn. There is also a problem that the noise and vibration caused by this is not smoothly engaged.

In addition, in the case of a planetary gearbox composed of an internal gear (hereafter referred to as a ring gear), the impact force or the concentrated load acted on the gear teeth when the gears are engaged with each other is relatively small compared to the gear trains of other principles, and a large number of teeth are engaged to make noise. And since the vibration is small, the volume is small, the input and output is concentric, and the power transmission efficiency is high, it is widely used in the fields of aircraft, automobiles, office equipment, machine tools, etc., which require small and light weight.

The planetary gear train consists of a sun gear, an internal gear, a planetary gear, and a carrier connecting the planetary gear shaft.The planetary gear train is a simple planetary gear train and a double planetary gear train or a multi-stage planetary gear train according to the number of pinions between the sun gear and the internal gear. It is divided into a composite planetary gear train comprising a. There may be various kinds of compound planetary gear sets, but three types described below are widely used.

First, the Simpson type composite planetary gear train has a combination of two single planetary gear trains. The two single planetary gear trains share the sun gear, and the ring gears of the first row and the planetary carriers of the second row are connected to the output shaft together. Input is selectively made via a planetary carrier in the first row, ring gears in the second row, and a common sun gear.

Second, the Ravigneaux type planetary gear train is a combination of a single planetary gear train and a double planetary gear train. The two rows share a ring gear and a planet carrier, and the planetary gears of the single planetary gear train are double planetary gears. It is integral with the planetary gears in the row of ring gears. Input is optionally via two independent sun gears and a common planet carrier, and output is through a common ring gear.

Third, the two simple type planetary gear train is a composite of two single planetary gear trains, but unlike the Simpson type, there is no shared element. The planetary carriers of the first row and the ring gears of the second row are connected, and the ring gears of the first row and the planetary carriers of the second row are connected to the output shaft together. Input is optionally made via two sun gears and a planetary carrier in the first row (ring gear in the second row).

The composite planetary gear train was developed for application to an automatic transmission of a vehicle, and has a relatively large and complicated configuration since at least five friction elements are required as a control element for shifting. In addition, the central axis including the sun gear is intended to act as a rotating element. This configuration is large and expensive to apply to bicycles or wheelchairs.

There are several proposals to apply planetary gearboxes to bicycles or wheelchairs.

Wheelchairs require considerable physical strength to drive left and right wheels with the power of their arms. Since the driving wheel and the circular push rim are usually fixed and the push rim is smaller than the wheel, the moment to be pushed is larger than the output moment required for the wheel. Even on slopes, wheelchairs are often unable to climb on their own. Therefore, various transmission apparatuses in which the rotational ratio between the wheel and the push rim are reduced so as to climb the slope even with a weak force and the load of the force is reduced have been proposed.

In the conventional shiftable manual wheelchair, the rotational drive from the push rim to the wheel is fixed at a specific reduction ratio, or, for example, it is proposed that multi-stage shifting is possible, such as US Patent 5362081 and Japanese Patent Application No. 2000-316914. Since it is difficult to achieve both speed shifting and transmission of the driving force to the wheels and cannot be freely shifted according to the road surface or driving conditions, it is not satisfactory to reduce the burden on the wheelchair operator. In addition, the transmission itself is complicated and expensive, heavy and has a high operating noise. Therefore, improvement is desirable for use in household goods and the like.

The present invention is to improve the above problems,

It is an object of the present invention to provide a transmission that is easily and quickly shifted during rotation, simple in structure, thin in thickness and light in weight, suitable for use in bicycles, wheelchairs or similar vehicles.

Further, another object of the present invention is to provide a general-purpose transmission that can be used comfortably and with low operating noise, which is required as a household article.

In order to achieve the above technical problem, the present invention is a combination of two planetary gear trains, the carrier of one planetary gear train and the ring gear of the other planetary gear train, respectively, and the two carriers are divided into a drive side and an output side to operate Two carriers cooperating to form a housing of the transmission, each of which includes a plurality of planetary gears; Two or more sun gears meshing with respective stages of the planetary gears and having a plurality of recesses formed on the inner circumferential surface for coupling with the home cam; A multistage transmission portion comprising: two ring gears engaged with the planetary gears; A central shaft on which the multi-speed transmission unit is installed; And a shift controller configured to selectively fix one of the plurality of sun gears to a central axis and to selectively integrate two adjacent ones of the plurality of sun gears.

Particularly, the planetary gear installed in the carrier is a double planetary gear including a plurality of planetary gears included in a simple planetary gear train and a plurality of other planetary gears externally engaged with the plurality of planetary gears, or the plurality of planetary gears. And a multi-stage planetary gear that includes a plurality of other planetary gears having a diameter different from that of the plurality of planetary gears, and a sun gear having a plurality of recesses engaged with the other planetary gears and engaging with the home cam on the inner circumferential surface thereof. It is preferable to include one or more.

The transmission of the present invention shifts by controlling the fixing of the sun gears with a plurality of sun gears as described above. When the sun gear is fixed, the gear ratio of driving side and output side is shown in Table 1 below.

  Fixed side   Driving side   Output side  Shifting rain  Simple planetary gear train  Double Planetary Gear Row  Multi-stage planetary gear train  Sun gear  carrier  Internal gear  Zr / (Zs + Zr) <1  -Zr / (Zs-Zr)> 1  1 + Zpr / Zr * Zs / Zps> 1  Internal gear  carrier  (Zs + Zr) / Zr> 1  (Zs-Zr) / (-Zr) <1 1 / (1 + Zpr / Zr * Zs / Zps) <1

     Zr: Number of teeth of internal gear Zs: Number of teeth of sun gear

     Zpr: Number of teeth in planetary gear stage in contact with ring gear

     Zps: Number of teeth of planetary gear stage in contact with sun gear

The drive side combines with a driven sprocket or similar device that is powered by a pushwheel of a wheelchair driven by a manpower or by a foot pedal of a bicycle to supply torque to the transmission. It is applicable to bicycles by providing a one-way clutch between the drive side and the input side of the transmission.

In addition, the central axis is configured to be quickly detached and mounted on the frame of the wheel of a wheelchair or bicycle, and has a structure that is installed so as not to rotate relative to the frame when mounted.

The shift control unit may include a shift sleeve surrounding the central axis and a respective cam groove for a home cam formed on a main surface thereof to guide an axial position of each home cam by a predetermined rotation; A home cam rotation direction fixing member fixed to the central shaft and having at least one guide groove extending in the axial direction to surround the shift sleeve; Inserted into the guide groove of the groove cam rotation direction fixing member is fixed in the rotation direction and moved along the cam groove of the shifting sleeve in the axial direction to move the sun gear in the axial direction or to engage with and separate from the central axis. It is preferably composed of more than ten home cam.

In this configuration, the two sun gears having the concave-convex portions on the opposite sides and the sun gears in the transmission are not fixed to the central axis. By joining and integrating the two sun gears, the two sun gears are integral with the planetary gears and at the same time with the ring gears. Therefore, the input torque is directly transmitted without shifting.

In addition, the shifting sleeve, in combination with a shifting handle provided in close proximity to the input side carrier rotates a predetermined angle by the shifting handle, and further comprises a holding mechanism (plunger) to maintain the position to control the position in the rotational direction You can shift. In particular, in the case of a wheelchair, the shift handle can be disposed near the input carrier push rim, which is easy to operate.

The shift sleeve has a through hole penetrating the central axis in the axial direction and a shift shaft disposed in the through hole, protruding from the frame, and having a shift knob fixed to the frame by a file or link mechanism or similar knitting. In combination with the protruding shift shaft, the shift knob can be shifted by rocking the shift knob.

The shift sleeve rotates by swinging the shift knob by enclosing the shift shaft and projecting past the housing and engaging the shift knob fixed to the frame with the rope or link mechanism or the shift shaft projected by similar knitting. You can shift by controlling the direction position.

The cam groove of the shifting sleeve is a groove which is continuously formed in a circumferential direction in a circumferential direction by mating with a groove cam rotational direction fixing member on a main surface of the shifting sleeve, and meshes with one of the sun gears according to the role of each of the grooved cams. Grooves inclined axially for guiding to a position, grooves continually guiding to positions not engaged with the two sun gears and lateral unevenness of the two sun gears in a position where the plurality of sun gears do not mate with a central axis; Guide grooves are formed in which the pressing portions axially engage with each other.

The shift sleeve may further include a spring for rotating the shift sleeve at an angle by pulling the shift knob, and returning the position of the shift sleeve when the pull by the knob is removed.

In the case of a wheelchair, the wheels are located at both sides of the vehicle body, and when the transmission of the present invention is mounted on the hub of the wheel, it is preferable to simultaneously control both transmissions. Thus, one or more of the planetary gear type transmission and the rope or link mechanism, or similar knitting are combined to the one shift knob, and the connected transmission is configured to shift simultaneously.

In addition, if the actuator is connected to the shift knob, and a sensor for detecting torque applied to the driving unit and a controller for judging according to the data of the sensor, the actuator can be automatically shifted by controlling the actuator. Can be provided.

The groove cam may be composed of a ring-shaped enclosing the rotation direction fixing member and a piece inserted into the guide groove of the rotation direction fixing member. In particular, the home cam made of pieces can minimize the size of the shift control unit.

The home cam has a convex for engaging with the recess of the sun gear, and moves in an axial direction to protrude a hidden protrusion, so that the protrusion works with the recess of the sun gear to reduce noise and resistance during the engagement. have.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described according to drawing. 1 is a perspective view illustrating a mounting state of a wheelchair wheel to which an embodiment of a four-speed planetary gear transmission according to the present invention is applied. FIG. 2 is an exploded perspective view illustrating components of the four-speed planetary gear transmission of FIG. 1 in an exploded manner.

The output carrier 17a, which serves as the center of the wheelchair wheel, is rotatably supported on the central axis 1 by bearings 17z ₁ and extends radially to provide one side wall of the transmission. On the side wall, three gear shafts 20 in a row of reduction gears are mounted to support three planetary gears 11. In addition, the output carrier 17 is fixedly coupled to and supported by the output carrier 17a so as not to surround the deceleration internal gear 13, which engages with the reduction planetary gear, and extends in the axial direction so as to be coupled to the acceleration internal gear 12. . The outer circumferential surface of the output carrier 17 is formed with a number of spoke holes for supporting the wheels. In addition, the output carrier 17a surrounds the bearing 17z ₁ and protrudes in the axial direction and has radial protrusions for engaging with the disk hub 111 on the outer circumferential surface thereof.

The input carrier 14, which tightly engages with the input side pushrim 16 so as not to rotate relatively, is supported by the bearing 14z on the central axis 1 and extends in the radial direction to provide the other side wall of the transmission. Three side grooves are formed in the side wall to support the planetary gear shaft 19 of the accelerated planetary gear train to support the three accelerated planetary gears 10. In addition to the acceleration planetary gear (10) Three grooves for supporting the planetary gear shaft 21 of the double planetary gear 22 which are externally installed are also arranged on the side wall. The double planetary gear 22 is circumscribed with the deceleration two-stage sun gear 23 disposed in contact with the side wall of the input carrier 14. Acceleration planetary gear 10 is extended in the axial direction in contact with the side wall of the input carrier 14 and the deceleration two-stage sun gear 23 and It is circumscribed with the accelerated sun gear 8 arranged side by side.

In addition, the input carrier internal gear holder 15 fixedly extended from the input carrier 14 is firmly coupled to the reduction internal gear 12 by welding or screws, and cooperates with the input carrier 14 to cooperate with the planetary gear shafts 19 and 21. I support it. The input carrier 14 supports the output carrier 17 with a bearing 17z ₂ and blocks the transmission from the outside with a retainer.

The inner circumferential surfaces of the acceleration sun gear 8, the reduction gear 1 sun gear 9, and the reduction gear 2 sun gear 23 have jaws that have a large radius (8b, 9b, 23b) and a small radius (8a, 9a, 23a). It has an inner circumferential surface. The inner circumferential surface 8a, 9a, 23a having a small radius surrounds the groove cam rotational direction fixing member 4 and is provided with a plurality of radial protrusions 8a, 9a for engaging with the radial protrusions 6f, 7f of the groove cams 6, 7. 23a is formed, and the inner circumferential surfaces 8b, 9b, and 23b having a large radius have a smooth inner circumferential surface so as to surround and rotate the radial protrusions 6f and 7f of the home cams 6 and 7. In addition, a plurality of projections 8c and 9c for axial engagement are formed on the side surfaces of the contacting sun gears 8 and 9. The two sun gears 8 and 9 move in the axial direction so that the axial protrusions 8c and 9c are engaged with each other and rotated together. At this time, the large inner circumferential surfaces 8b and 23b of the two sun gears are configured to rotate while accommodating the first grooved cam 6.

The central shaft 1 having the axial through hole 1a has a small radius shaft portion having, at one end, a stepped jaw 1b in contact with an inner ring side surface of the bearing 14z supporting the input carrier 14. And a small radius shaft is formed at the opposite end to engage the vehicle body. In the middle part of the central axis where the small radius and the large radius meet, a flat ring 1c is formed in the large radius shaft to prevent rotation of the shaft with respect to the frame, and then a snap ring supporting the inner ring side of the bearing 17z supporting the output carrier. The groove 1d is formed. In addition, two to four radial through holes 1g are formed at the end portions of the small radius shaft to accommodate the balls 26 for fixing the central shaft 1 to the vehicle body. At the opposite end, the jaw 2c supports the ball 26 to protrude from the central axis 1 when the central axis 1 is fixed to the vehicle body 100, and the ball 26 is separated from the vehicle body. A recessed groove 2d for accommodating the shaft is formed.

A spring 5 is disposed between the central axis 1 and the shifting sleeve 3 to provide the rotational direction elasticity so that the central axis 1 and the shifting sleeve 3 are fixed in the rotational direction. When the wheel is separated from the body 100 by this, the transmission shaft 1 is always located in the first stage of acceleration and guides the coupling to the first stage of acceleration when mounted on the body 100. In addition, the outer diameter of the shifting shaft coupling ring 25 is smaller than the small outer diameter of the central shaft 1 for attachment and detachment of the wheel, and a radial protrusion is formed to engage with the shifting strap 30.

Inside the bearing 17z supporting the center 17 of the wheel, the shifting sleeve 3 is supported on the central shaft 1 and is rotatably installed. The side of the shift sleeve 3 is formed with a projection 3c for projecting the housing to engage with the shift strap. On the main surface, three sets of cam guide grooves for the first groove cam 6 and the second groove cam 7 are formed in two rows. In the present embodiment, the guide groove of the first grooved cam 6 is located between 0 ° and 5 °, and the first grooved cam 6 is located in a neutral position between the accelerated sun gear 8 and the reduced-speed two-stage sun gear, and 25 ° to 30 °. Induces the accelerated sun gear (8) to engage the deceleration 1st stage sun gear and is positioned out of engagement with both sun gears (8, 23) at 55 ° to 65 °, and the deceleration 2nd sun gear (85 to 90 °) 23) is meshed with. In addition, the guide groove of the second groove cam (7) is engaged with the acceleration sun gear (8) at 0 ° ~ 5 °, is located between the two sun gear (8, 9) at 25 ° ~ 35 °, 55 ° ~ It meshes with the first gear of the reduction gear at 65 ° and is not engaged between the two sun gears 8 and 9 at 85 ° to 90 °. Three sets of guide grooves 3a and 3b of the shift sleeve 3 are arranged in the circumferential direction from 0 °, 120 ° and 240 °, respectively, which are pinched or tilted while the home cams 6 and 7 are moved in the axial direction. This is to make it work smoothly without losing.

The groove cam rotational direction fixing member 4 is fixed to the center shaft 1f on the inner side of the bearing 14z by a key 21 so as not to rotate, and the three projections are guide grooves 3b of the shifting sleeve 3; 3c, 3d, and 3e) extends side by side in the axial direction so as not to meet 3c, 3d, and 3e.

The first groove cam 6 has a concave groove 6b for accommodating the pin 6a for engaging the guide groove 3b of the shift sleeve 3 and an axial guide surface for engaging the groove cam rotational direction fixing member 4. 6d) is formed on the side surface and is immersed in the groove of the home cam rotation direction fixing member 4, and consists of three pieces. Further, the outer circumferential surface 6c is provided with a radial projection 6f for engaging with the inner circumferential surface radial projection of the deceleration two-stage sun gear 23 and a step 6g for pressing the acceleration one-stage sun gear in the axial direction. Accordingly, the first groove cam 6 is engaged with the shift sleeve 3 by the pin 6a and the rotation groove 3 does not rotate by the home cam rotation direction fixing member 4 as the shift sleeve 3 rotates. Move axially along 3b) to pressurize the bearing 9z and the accelerated first-stage sun gear 8 in the axial direction and engage the deceleration first-stage sun gear 9.

The second groove cam 7 has a concave groove 7b for accommodating the pin 7a for engaging with the guide groove 3a of the shift sleeve 3 and an axial guide surface for engaging the groove cam rotational direction fixing member 4. 7d) is formed in the side surface and is immersed in the groove | channel of the home cam rotation direction fixing member 4. Further, on the outer circumferential surface 7c, radial projections 7f for engaging with the inner circumferential surface radial projections of the sun gears 8 and 9 are formed. Accordingly, the second groove cam 7 is engaged with the shift sleeve 3 by the pin 7a and the second groove cam guide groove is not rotated by the home cam rotation direction fixing member 4 as the shift sleeve 3 rotates. Along the axial direction.

The wheel center shaft support 27 may have various shapes in accordance with the shape of the vehicle body 100 to fix the wheels to the vehicle body 100. In the present embodiment, the U-shaped groove 27a is made to be mounted and mounted on the round bar-shaped vehicle body 100 and fixed to the vehicle body 100 by passing a screw through the round bar. In addition, a through hole 27b for supporting the central axis 1 of the wheel is formed in the outward direction of the vehicle body 100, and a plane engaging with the plane of the central axis 1 outside the through hole 27b. The protruding portion 27d is supported so that the central axis 1 does not rotate, and the middle portion is formed with a stepped jaw that accommodates the ball 26 protruding from the central axis in order to fix the central axis to the vehicle body. In addition, a shifting strap 30 is provided on the outer circumferential surface of the flat protrusion, and a stepped jaw 27e for accommodating the concentric disc hub 111 and a snap ring groove 27c for supporting the concentric disc hub 111 are formed. It is. In addition, the transmission strap 30 is pressurized by the spring 24.

Transmission strap 30 is coupled to the shifting knob (not shown) and one shifting line 35 installed around the armrest of the occupant is configured to swing together in cooperation with the spring 24 when the shifting knob is rocked by the occupant . The shifting line 35 is wound between the outer ring of the shifting strap 30 and the shifting line fixing plate 32 by passing through the shifting guide plate 32 attached to the wheel center shaft support 27 from the shifting knob. 32).

The disc hub 111 is connected to a brake system for braking the vehicle. The small inner circumferential surface is supported to the wheel center shaft support and is installed to rotate. In addition, the large inner circumferential surface has a radial projection for transmitting rotational force in combination with the output carrier 17. On the outer circumferential surface, a stepped jaw for fixing the disk 112 is formed, and a radial screw hole is formed at the side thereof. The disc hub rotates by screwing the disc together. The disc is engaged with the caliper 112 to control the rotation of the wheel.

Referring to the operating state of the transmission using the planetary gear of the present invention.

FIG. 5 is a partial cross-sectional view showing a constant speed driving state without a shift of the four-speed planetary gear transmission of the present invention, and FIG. 6 is a cross-sectional view taken along the line BB of FIG. 3.

When the wheelchair wheel is mounted on the wheelchair 100, the spring 24 guides the shift shaft coupling ring 25 to a neutral position so that the shift shaft 2 is in a direct position. The main shaft 1 of the wheelchair wheel is inserted into the through hole 27b of the wheel center shaft support 27 with the shift shaft 2 pulled out, and when the shift shaft 2 is released, the spring 24 acts as a function of the spring 24. The central shaft 1 is fixed to the wheel central shaft support 27 by the ball 26 protruding from the transmission shaft 2. At the same time, the shifting shaft 2 is connected to the shifting strap 30 through the shifting shaft coupling ring 25.

The second groove cam 7 of the transmission coupled in the constant speed drive mode moves the bearing 9z and the deceleration sun gear 9 toward the acceleration sun gear 8 by the shift sleeve 3 and the groove cam rotation direction fixing member 4. The two sun gears 8 and 9 are pushed together to be united, and the guide groove 3e of the second grooved cam supports the tooth not to be released. The first groove cam 6 is disposed between the spaces 8d and 9d in which the acceleration sun gear 8 and the reduction sun gear 9 are integrally formed by the shifting sleeve 3 and the groove cam rotation direction fixing member 4. Avoid contact with the sun gear. Therefore, the two sun gears 8 and 9 do not engage with the central axis 1, and at the same time, two planetary gear trains supported by the bearings 14z and 17z on the central axis 1 can freely rotate.

At this time, when a rotational force is input from the push rim 16, the rotational force is transmitted to the four planetary gear shafts 19 via the input carrier 14. This rotational force is transmitted to the acceleration internal gear 12 and the acceleration sun gear 8 through the acceleration planetary gear 10 and at the same time the speed reduction internal gear (15) through the input carrier internal gear holder 15 coupled with the planetary gear shaft 19. 13) is delivered. At this time, since the acceleration sun gear 8 is integrated with the deceleration sun gear 9, the deceleration sun gear 9 and the deceleration internal gear 13 are turned together so that the transmission of the present invention is a direct drive (direct drive) ( When planetary gears rotate any two gears at the same time, the third gear is directly connected in the same direction and at the same speed). Accordingly, the wheel 17 and the push rim 16 are freely supported on the central shaft 1, and the input carrier 16 and the output carrier 17 are directly connected, so that the rotation of the push rim 16 is performed. Rotates in a constant velocity drive state that is directly transmitted to the wheels 17.

3 is a partial cross-sectional view showing the acceleration state of the three-speed planetary gear transmission of the present invention, Figure 4 is a cross-sectional view taken along the line A-A of FIG.

When the passenger selects the acceleration mode by operating the shift knob in the constant speed driving state, the speed change line 36 is pulled and the speed change line 35 is loosened, so that the speed line strap (rotated to the wheel center shaft support 27) is installed. 30 is rotated, and the shift key 5 is rotated counterclockwise as shown in FIG. 4 through the shift shaft coupling ring 25 / shift shaft 2 / shift key 5 integrally coupled with the shift catch 30. Will rotate.

When the shifting key 5 rotates, the shifting sleeve 3 also rotates so that the guide groove of the second grooved cam rotates. The second groove cam 7 which is not rotated by the groove cam rotation direction fixing member 4 moves toward the output carrier 17 along the guide groove 3f along with the ball 7a of the second groove cam coupled to the guide groove. Release the axial pressurization of the two sun gears 8, 9. The two sun gears 8 and 9, which are released from the restraint, are rotated in opposite directions so that the teeth are released and separated. (At this time, the two planetary gear trains are in a state where the torque cannot be transmitted because there is no fixed element, but there is no rotational force input from the push rim since the handle is manipulated to shift the passenger.)

Subsequently, the guide grooves 3c-> 3b of the first groove cam, which rotate together with the guide grooves of the second groove cam, accelerate the first groove cam 6 that is not rotated by the groove cam rotational direction fixing member 4 to accelerate the sun gear ( It guides to the position which engages with the inner peripheral surface protrusion 8b of 8). Accordingly, the first home cam 6 and the acceleration sun gear 8 are engaged with each other, and the acceleration sun gear 8 is fixed to the central axis 1 to be in an acceleration shift state. At this time, since the acceleration sun gear 8 rotates at a relatively low speed while the rotation is performed, and the projections of the entire main surface are coupled at a time, shifting is smoothly performed because friction noise or resistance due to the coupling does not occur.

When a rotational force is input from the push rim 16 while the gear is shifted in the acceleration mode, the rotational force is transmitted to the four planetary gear shafts 19 via the input carrier 14. This rotational force is transmitted to the acceleration internal gear 12 and the acceleration sun gear 8 via the acceleration planetary gear 10. It is also transmitted to the deceleration internal gear 13 through the input carrier internal gear holder 15 and to the deceleration planetary gear 11 and the deceleration sun gear 9, but without the fixed element, the deceleration planetary gear train is idle. Therefore, only the acceleration planetary gear train is operated and the rotational force is transmitted to the output carrier 17 coupled with the acceleration internal gear 12 according to the transmission ratio.

When the passenger again selects the constant speed mode by operating the shift knob, the deceleration shifting line 35 is pulled and the acceleration shifting line 36 is loosened, so that the shifting strap 30 installed on the wheel center shaft support 27 rotates. The shift key 5 is rotated counterclockwise through the shift shaft coupling ring 25 / shift shaft 2 / shift key 5 which is integrally coupled with the shift strap 30 and rotates as shown in FIG. 6. Return to the direct connection mode position.

The process of shifting from the acceleration mode to the constant speed mode is the reverse of the process of shifting from the constant speed mode to the acceleration mode, and thus will be omitted. In this shifting process, after the first home cam 6 is released from the acceleration sun gear 8, the acceleration sun gear 8 and the deceleration sun gear 9 are combined in the axial direction to be integrated. Even though each element is rotating at different speeds in each disengagement and engagement, each of them rotates at a relatively low speed and the entire projection is separated or engaged at once, so that the shifting is smooth because no friction noise or resistance due to the engagement occurs. .

FIG. 7 is a partial cross-sectional view illustrating a deceleration state of the three-speed planetary gear transmission of FIG. 1, and FIG. 8 is a cross-sectional view taken along the line CC of FIG. 7.

When the passenger selects the deceleration mode by operating the shift knob in the constant speed driving state, the deceleration shifting line 35 is pulled, and the acceleration shifting line 36 is loosened, and thus the shifting liner installed on the wheel center shaft support 27 is rotated. 30 is rotated, and the shift key 5 is clockwise as shown in FIG. 8 through the shift shaft coupling ring 25 / shift shaft 2 / shift key 5 integrally coupled with the shift catch 27. Will rotate.

When the shifting key 5 rotates, the shifting sleeve 3 also rotates so that the guide grooves 3e, 3f, and 3g of the second groove cam 7 rotate. The second groove cam (7), which is not rotated by the groove cam rotation direction fixing member (4), is disposed along the guide groove (3e-> 3g) along with the guide groove (3e-> 3g) of the second groove cam coupled to the guide groove. To release the axial pressurization of the two sun gears 8, 9. The two sun gears released from the restraint rotate in opposite directions, releasing the teeth and separating them. (At this time, the two planetary gear trains are in a state where the torque cannot be transmitted because there is no fixed element, but there is no rotational force input from the push rim since the handle is manipulated to shift the passenger.)

Subsequently, the guide grooves 3b, 3c, and 3d of the first groove cam, which rotate together with the guide groove of the second groove cam, decelerate the first groove cam 6 which is not rotated by the groove cam rotation direction fixing member 4. It guides to the position which engages with the inner peripheral surface protrusion 9b of (9). Therefore, the first home cam 6 and the reduced speed sun gear 9 mesh with each other, and the reduced speed sun gear 9 is fixed to the central axis 1. At this time, even if the deceleration sun gear 9 is rotated, the projections of the entire main surface are temporarily coupled, so that the frictional noise or resistance due to the coupling does not occur, and thus shifting is smoothly performed.

When the rotational force is input from the push rim 16 while the gear is shifted in the deceleration mode, the rotational force is transmitted to the four planetary gear shafts 19 via the input carrier 14. This rotational force is transmitted to the acceleration internal gear 12 and the acceleration sun gear 8 via the acceleration planetary gear 10, but without the fixed element, the acceleration planetary gear train is idle and coupled to the planetary gear shaft 19. The output is transmitted to the deceleration internal gear 13 through the input carrier internal gear holder 15 and to the deceleration planetary gear 11 and the deceleration sun gear 9 so that only the deceleration planetary gear train is operated to be combined with the deceleration planetary gear shaft. The rotational force is decelerated and transmitted to the carrier 17 according to the transmission ratio.

When the occupant selects the direct connection mode by manipulating the shift knob, the acceleration shift string 36 is pulled and the deceleration shift string 35 is loosened, so that the shift strap 30 installed on the wheel center shaft support rotates, The shift key is rotated counterclockwise as shown in FIG. 6 through the shift shaft coupling ring / shift shaft / shift key integrally coupled with the shift strap to return to the direct mode position. The process of shifting from deceleration mode to direct mode is omitted since it is the reverse of the process of shifting from direct mode to deceleration mode.

The above preferred embodiments are illustrated and described for the purpose of illustrating not only the structural and functional technical ideas of the present invention, but also for the purpose of illustrating the method of using the preferred embodiments. It can be changed without implementation. Accordingly, the invention is intended to embrace all such modifications as fall within the scope of the spirit of the appended claims.

According to the present invention, since the carrier serves as the transmission housing, the vehicle is small and light, and the central shaft can be attached to or detached from the vehicle body, and a direct mode and a power transmission system in which power is transmitted without deceleration mode, acceleration mode and shifting without using a clutch. In combination with the vehicle body, there is provided a planetary gear transmission having a stop mode that does not rotate.

In particular, when the present invention is applied to the wheel of the wheelchair, the occupant may shift at a low speed to easily climb a hill or travel on a sand field or a carpet with a small force, and may shift at a high speed to travel more flat.

Claims (20)

By combining two planetary gear trains, the carriers of one planetary gear train and the ring gears of the other planetary gear trains are integrated, respectively, and the two carriers, which are divided into a driving side and an output side, cooperate to form a housing of a transmission. Two carriers on which a plurality of planetary gears are installed; Two or more sun gears meshing with respective stages of the planetary gears and having a plurality of recesses formed on the inner circumferential surface for coupling with the home cam; A multistage transmission portion comprising: two ring gears engaged with the planetary gears; A central shaft on which the multi-speed transmission unit is installed; A planetary gear transmission configured to selectively fix one of the plurality of sun gears to a central axis and to selectively integrate two adjacent ones of the plurality of sun gears. The planetary gear of claim 1, wherein the planetary gear installed in the carrier further includes a plurality of planetary gears included in a simple planetary gear train and a plurality of other planetary gears externally engaged with the plurality of planetary gears. Planetary gear type transmission characterized in that it further comprises at least one sun gear meshing with the gear and formed with a plurality of recesses for engaging the home cam on the inner circumferential surface The planetary gear installed in the carrier includes a plurality of planetary gears included in a simple planetary gear train, and a plurality of other planetary gears having a diameter different from that of the plurality of planetary gears. The planetary gear type transmission further includes one or more sun gears engaged with the other planetary gears and having a plurality of recesses formed on the inner circumferential surface thereof to engage the home cams. The planetary gear type transmission according to claim 3, wherein a plurality of planetary gears included in the simple planetary gear train and a plurality of other planetary gears having different diameters are directly connected to each other. The planetary gear type transmission according to claim 1, wherein the driving side carrier is combined with a driven sprocket which is driven by a force driven push rim or foot pedal. The method of claim 1, wherein the central axis, The planetary gearbox is configured to be quickly detached and mounted to the frame and is installed so as not to rotate relative to the frame when mounted. The method of claim 1, wherein the shift control unit, A shift sleeve surrounding the central axis and having respective cam grooves formed on the main surface thereof for guiding the axial positions of the respective home cams by a predetermined rotation; A home cam rotation direction fixing member fixed to the central shaft and having at least one guide groove extending in the axial direction to surround the shift sleeve; Inserted into the guide groove of the groove cam rotation direction fixing member is fixed in the rotation direction and moved along the cam groove of the shifting sleeve in the axial direction to move the sun gear in the axial direction or to engage with and separate from the central axis. Planetary gear transmission, characterized in that consisting of; 8. The two sun gears of claim 7, wherein the two sun gears are pressed in the axial direction by the home cam in a state in which the two sun gears having the uneven portions on the opposite sides and all the sun gears in the transmission are not fixed to the central axis. Planetary gearbox characterized in that the gears engage with each other and integrate the two sun gears The method of claim 7, wherein the shift sleeve, Planetary gears characterized in that the rotational direction is controlled by a configuration further comprising a holding mechanism (plunger) to rotate a predetermined angle by the shifting handle in combination with the shifting handle provided in close proximity to the input side carrier, to maintain the position Expression gearbox The method of claim 7, wherein the shift sleeve, A through shaft penetrating the central axis in the axial direction and a shift shaft disposed in the through hole and protruding from the frame, the shift shaft being fixed to the frame by a file or link mechanism, or similar knitting; And a planetary gear type transmission characterized in that the rotational direction is controlled by rocking the shift knob. The method of claim 7, wherein the shift sleeve, The rotational direction is controlled by swinging the shift knob by enclosing the central axis and projecting past the housing, and engaging the shift knob fixed to the frame with a rope or link mechanism or a similar knitting. Planetary gear transmission characterized in that The method of claim 9, wherein the cam groove of the shift sleeve, A groove formed on the main surface of the shift sleeve in a concave shape in a circumferential direction to mate with the rotational direction of the cam rotation direction, and axial direction for guiding to the position to engage with one of the sun gears according to the role of each of the groove cams. The grooves inclined to the grooves, the grooves continually guiding to positions not engaged with the two sun gears, and the lateral convex portions of the two sun gears axially engage with each other at a position where the plurality of sun gears do not engage the central axis. Planetary gear type transmission characterized in that the guide groove for pressing is formed The method of claim 10 or 11, The shift sleeve rotates at an angle by pulling the shift knob, and when the pull by the knob is removed, the planetary gear type transmission further comprises a spring for returning the position of the shift sleeve. 14. The planetary gear according to claim 13, wherein the shift knob is coupled by one or more of the planetary gear type transmission with a string or link mechanism, or a similar knitting, and the transmission connected by the one shift knob is simultaneously shifted. Expression gearbox 15. The method of claim 14, wherein the shift knob is coupled to the actuator, the sensor for detecting the torque applied to the drive unit; The planetary gear type transmission comprising a controller for judging according to the data of the sensor and controlling the actuator. 8. The planetary gear type transmission of claim 7, wherein the home cam has a ring shape surrounding the home cam rotation direction fixing member. 8. The planetary gear transmission according to claim 7, wherein the groove cam is made of a piece inserted into the guide groove. 18. The planetary gear transmission according to claim 16 or 17, wherein the home cam has a convex portion for engaging with the recess of the sun gear. 18. The planetary gear type transmission according to claim 16 or 17, wherein the projections hidden in the home cam groove cam are protruded so that the projections engage with the recesses of the sun gear. The planetary gear transmission according to claim 5, wherein a one-way clutch is provided between the drive side carrier and the driven sprocket.

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