KR20110012738A - Planetary gear transmission and vehicle using same - Google Patents

Abstract

PURPOSE: A planetary gear transmission and a vehicle using the same are provided to reduce weight by using a carrier as a housing of a transmission. CONSTITUTION: Two single planetary gear rows are combined. One carrier(17) are integrated with a ring gear of the other side. The housing of a transmission is comprised by combining two carriers which are operated in an input side and an output side. An adjacent sun gear is integrated or separated for changing a speed. A planetary gear(22) is comprised of a complex planetary gear. The planetary gear is comprised of a sun gear(23) with a plurality of concave parts for combining with a center shaft.

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 of the wheelchair b) perspective view from the inside of the wheelchair

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.

FIG. 7 is a cross-sectional view taken along the line C-C of FIG. 5 to show the state in which the sun gear 23 is fixed and decelerates in two steps.

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

6: First Homecam 7: Second Homecam 8: Accelerated Sun Gear

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

11: Reduced gear 1 planetary gear 12: Output gear ring

13: Ring gear with input career 14: Input career

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

17: output career (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 center shaft

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, a career is small and light as the transmission housing, and the central shaft is detachable from the 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. Among the gearboxes using a gear, a spur gear, a helical gear, and a gear train are used. 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 when the gears are rotated according to the engagement between the gears, and in particular, only a part of the teeth is formed compared to the total number of teeth formed on the outer peripheral surface. There is also a problem that the noise and vibration caused by this is not smoothly engaged between the gears.

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, a career connecting the planetary gear shaft, etc., and the simple planetary gear train and the double planetary gear train or the multi-plane 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 career of the second row are connected to the output shaft together. Input is selectively made through the planetary career in the first row, the ring gear in the second row and the 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, and these two rows share a ring gear and a planetary career, and the planetary gears of the single planetary gear train are double planetary. It is integrated with the planetary gears that are bitten by the ring gear of the gear train. Inputs are optionally made via two independent sun gears and a common planetary career, while outputs are made 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 career of the first row and the ring gear of the second row are connected, and the ring gear of the first row and the planetary career of the second row are connected to the output shaft together. Input is optionally made via two sun gears and a planetary career 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.

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 has a radius 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 four or more speed transmission, which is easily and quickly shifted during rotation, is simple in structure, thin and light, and suitable for use in bicycles, wheelchairs or similar vehicles.

In addition, another object of the present invention is to provide a general-purpose transmission that can be used comfortably and with low operating noise.

In order to achieve the above technical problem, the present invention combines two single planetary gear trains, integrates one career and the other ring gear, respectively, and cooperates with the two careers divided into the input side and the output side to cooperate with the housing of the transmission. And combining or separating each of the sun gears rotatably installed on a fixed central axis with the central axis, and controlling the uniting or separating the adjacent sun gears to shift the gears, in particular installed in each career The planetary gear is at least one of which is a composite planetary gear; and three or more sun gears engaged with respective stages of the planetary gear and having a plurality of recesses formed on the inner circumferential surface thereof for coupling with the central axis.

In particular, the planetary gear installed in the career may be 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

career
Internal gear
Zr / (Zs + Zr) <1
-Zr / (Zs-Zr)> 1
1 + Zpr / Zr * Zs / Zps> 1
Internal gear
career
(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

A mechanism for coupling or separating each sun gear with the central axis, and for integrating or separating the two sun gears, each cam groove for the home cam is formed on the main surface and surrounds the central axis, and the respective home cams are rotated by a predetermined angle. A shift sleeve guiding an axial position of the shift sleeve; 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 transmitted directly without shifting.

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 home cam is inserted into the guide groove, and has a convex portion to be engaged with the recess of the solar gear, so that the protrusion is engaged with the recess of the sun gear, thereby reducing noise and resistance during the engagement.

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 career 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 and the other side wall 17b of the output career, three gear shafts 20 of the reduction gear row are mounted to support the three planetary gears 11. In addition, the output career 17 is fixedly coupled to the output career 17a in the axial direction and the rotational direction, and is enclosed from the outside so as not to contact the reduced speed internal gear 13 engaged with the speed reduction planetary gear and expanded in the axial direction to accelerate the internal gear. Fix it with 12. At both ends of the output career 17, a number of spoke holes for supporting the wheels are formed. The output career 17a also has a radial projection 17c surrounding the bearing 17z and protruding in the axial direction to engage the disk hub 111 on the outer circumferential surface thereof.

The input career 14, which tightly engages with the input side pushrim 16 so as not to rotate relatively, is supported by the bearing 14z to the central shaft bearing support 1b 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. Acceleration planetary gear 10 is extended in the axial direction in contact with the side wall of the input career 14 and the deceleration two-stage sun gear 23 and It is circumscribed with the acceleration sun gear 8 arranged side by side. 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 arranged in contact with the side wall of the input career 14 but is not engaged with the accelerated internal gear 12.

In addition, the input career internal gear holder 15, which is fixedly extended from the input career 14, is firmly coupled to the reduction internal gear 13 by welding or screws, and cooperates with the input career 14 to form the planetary gear shafts 19 and 21. I support it. The input career 14 supports the output career 17 with a bearing 17zz 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 protrusions may be in the shape of triangles, squares or rhombuses as shown. The two sun gears 8 and 9 move in the axial direction and are arranged to rotate together when the axial protrusions 8c and 9c mesh with each other. 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 the inner ring side surface of the bearing 14z supporting the input career 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 plane ring 1c for preventing rotation of the shaft with respect to the frame is formed in the shaft of the large radius, and then a snap ring for supporting the inner ring side of the bearing 17z supporting the output career. The groove 1d is formed. In addition, two to four radial through holes 1g are formed at the end of the small radius shaft to accommodate the balls 26 for fixing the central shaft 1 to the vehicle body. The ball 26 protrudes from the central axis 1 at the time of fixing to the central axis 1 and is formed to accommodate the ball 26 into the central axis at the time of separation. In addition, the outer diameter of the transmission 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 transmission strap 30.

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.

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 at a neutral position between the accelerated sun gear 8 and the decelerated two-stage sun gear at 0 ° to 10 °, and 20 ° to 40 °. 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 50 ° ~ 70 °, and the deceleration 2nd sun gear (80 ° ~ 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 ° ~ 10 °, is located between the two sun gear (8, 9) at 20 ° ~ 40 °, 50 ° ~ It is engaged with the first gear of reduction gear at 70 ° and is not engaged between two sun gears (8, 9) at 80 ° ~ 90 °. The guide grooves 3a and 3b of the shifting sleeve 3 are arranged in three pairs starting at 0 °, 120 ° and 240 ° in the circumferential direction, respectively, so that the home cams 6 and 7 are pinched or tilted while moving in the axial direction. Keep it running smoothly.

The groove cam rotational direction fixing member 4 is fixed to the central axis 1f on the inside of the bearing 14z by a key 21 so as not to rotate, and the three projections 4a are guide grooves of the shifting sleeve 3. It surrounds (3b, 3c, 3d, 3e) and extends side by side in the axial direction. The side surface 4b of the protrusion is in contact with the side surfaces 6d and 7d of the home cam, and guides the home cams 6 and 7 to move in the axial direction.

The first groove cam 6 is formed with a concave groove 6e for receiving a pin PIN or a ball 6a for engaging the guide groove 3b of the shifting sleeve 3 on the inner circumferential surface thereof. On the outer circumferential surface 6d of the axial guide surface 6d and the outer circumferential surface contacting the home cam rotational direction fixing member 4b, a radial protrusion 6f for coupling with the radial protrusion of the inner circumferential surface of the reduction gear 2 sun gear 23 and the acceleration 1st stage sun gear A stage 6g for pressurizing in the axial direction is formed. These three first groove cams are disposed between the grooves of the home cam rotational direction fixing member 4 and the shift sleeve 3. Therefore, the first groove cam 6 is coupled to the shifting sleeve 3 by the pin 6a, and as the shift sleeve 3 rotates, the first groove cam guide groove does not rotate by the groove cam rotation direction fixing member 4. Moving along the axis 3b in the axial direction, the bearing 9z and the acceleration one-stage sun gear 8 are pressed in the axial direction so as to engage with the deceleration one-stage sun gear 9.

The second groove cam 7 has a concave groove 7b for receiving a pin PIN or a ball 7a for engaging the guide groove 3a of the shifting sleeve 3 on an inner circumferential surface thereof. On the axial guide surface 7d and the outer circumferential surface 7c in contact with the home cam rotational direction fixing member 4b, radial projections 7f for engaging with the inner circumferential surface radial projections of the sun gears 8 and 9 are formed. These three second groove cams are arranged between each groove of the home cam rotational direction fixing member 4 and the shift sleeve 3. 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 mount the wheel on the vehicle body 100. In this 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. This shape allows the wheels to be easily and quickly mounted and removed from the bodywork. 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 a spring (34).

Transmission strap 30 is coupled to the shifting knob (not shown) and the shifting line 35 is installed around the armrest of the occupant is configured to swing as the shifting knob swings by the occupant. The transmission line 35 passes through the transmission line guide plate 32 attached to the wheel center shaft support 27 from the shift handle and is wound around the outer circumferential surface of the transmission line catch 30 and fixed by the transmission line fixing screw 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 27 is installed to rotate. In addition, the large inner circumferential surface has a radial projection for transmitting rotational force in combination with the output career 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.

5 is a partial sectional view showing a constant speed driving state without a shift of the four-speed double planetary gear type transmission of the present invention.

After the wheelchair wheel is mounted on the wheelchair 100, the shift sleeve 3 is in a direct connection position by guiding the wheel to a neutral position through the shift knob to operate in the constant speed driving mode. While pressing the central axis pin (2), the central axis (1) of the wheelchair wheel is inserted into the through hole (27b) of the wheel center axis support (27), and when the central axis pin (2) is released, the spring (2d) The central shaft 1 is fixed to the wheel central shaft support 27 by the ball 26 which is pushed by the fixing pin 2c to protrude.

The first groove cam 6 of the transmission coupled in the constant speed drive mode is moved 6 ^'" by the shift sleeve 3 and the groove cam rotation direction fixing member 4 to reduce the acceleration sun gear 8 to the first gear of the reduction gear ( 9) The two sun gears 8 and 9 are pushed toward each other, and the guide grooves of the first grooved cam support the accelerated sun gear so that the teeth are not released. The second grooved cam 7 is freely rotated without contact with the home cam 6. The second grooved cam 7 is accelerated by the gear 8 and the rotational direction fixing member 4 of the home cam. The gear 9 is located at 7 ^" so as not to contact the two sun gears between the spaces 9b which are integrally formed. 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 9z, 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 three planetary gear shafts 19 via the input career 14. This rotational force is transmitted to the output career ring gear 12, the acceleration sun gear 8, and the deceleration two-stage sun gear 23 through the acceleration planetary gear 8, and the input career ring combined with the planetary gear shaft 19. It is transmitted to the ring carrier 13 with an input career through the gear holder 15. At this time, since the accelerated sun gear 8 is integrated with the reduced speed sun gear 9, the reduced speed sun gear 9 and the reduced speed internal gear 13 rotate together to form a direct drive (the planetary gear train is a ring). When two gears of the gear, planetary gear, and sun gear are rotated at the same time, the other gear is directly connected in the same direction and at the same speed.) Accordingly, the wheel center 17 and the push rim 16 connected to the wheels and spokes are freely supported on the central axis 1, and the input career 16 and the output career 17 are directly connected to each other. The rotation of the push rim 16 thus rotates in a constant velocity drive state that is directly transmitted to the wheels 18.

3 is a partial cross-sectional view showing an acceleration state of a four-speed double planetary gear type transmission of the present invention, and FIG. 4 is a cross-sectional view along the line AA of FIG. 3.

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 reduction line 35 is loosened, so that the speed transmission liner is installed to rotate on the wheel center shaft support 27. 30 rotates, and the shift sleeve 3 integrally coupled with the shift catch 30 is rotated counterclockwise.

When the shift sleeve 3 rotates, the guide groove of the second groove cam also rotates. The first groove cam 6, which is not rotated by the groove cam rotational direction fixing member 4, moves along 6 ^" to the input groove along the guide groove 4b together with the ball 6a of the first groove cam coupled to the guide groove. 14 to release the axial pressurization of the two sun gears 8 and 9. The two sun gears 8 and 9 released from the restraint are moved in opposite directions by the elastic force to the elastic member so that the tooth is released and separated. (At this time, the two planetary gear trains are in a state in which there is no fixed element, so the torque cannot be transmitted, but there is no rotational force input from the push rim since the handle is operated for shifting the passenger's body.) Is not in contact with the first home cam (6) is a state that can rotate freely.

In addition, the guide groove 3a of the second groove cam, which rotates together with the guide groove of the first groove cam, has an inner circumferential surface of the sun gear 8 that accelerates the second groove cam 7 which is not rotated by the groove cam rotation direction fixing member 4. Guide to position 7 ^′ engaging projection 8b. Therefore, the second groove cam 7 and the acceleration sun gear 8 are engaged, and the acceleration sun gear 8 is fixed to the central axis 1 to be in an acceleration shift state. At the same time, the deceleration first stage sun gear 9 is in a state of being free to rotate without contacting the second groove cam 7. 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 the 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 three planetary gear shafts 19 via the input career 14. This rotational force is transmitted to the output career-attached ring gear 12 and the acceleration sun gear 8 via the acceleration planetary gear 10. It is also transmitted to the input career ring gear 13 through the input career ring gear holder 15 and to the reduction gear 1 planetary gear 11 and the reduction gear 1 sun gear 9, but without the fixed element. The gear train is idle. Therefore, only the acceleration planetary gear train is operated so that the rotational force is transmitted to the output career 17 combined with the output career-attached ring gear 12 in accordance with 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 shifting sleeve 3 which is rotated and integrally coupled with the shifting strap 30 is rotated counterclockwise to return to the direct connection mode position as shown in FIG. 5.

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 first-stage sun gear 9 are axially coupled to form an integrated body.

FIG. 6 is a partial cross-sectional view showing a first speed reduction state of a four-speed double planetary gear type transmission of FIG. 1, taken along line BB of FIG. 3.

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 rotates, and the shift sleeve 3 integrally coupled with the shift catch 27 is rotated clockwise.

When the shift sleeve 3 rotates, the guide groove 3b of the first groove cam 6 rotates. The first groove cam 6, which is not rotated by the groove cam rotation direction fixing member 4, has a 6 ^" position along the guide groove 3b with the pin 6a of the first groove cam coupled to the guide groove. To release the axial pressurization of the two sun gears 8 and 9. The two sun gears released from the restraint are rotated in opposite directions and the engagement is released and separated by the elasticity of the elastic member. However, the sun gear 23 is free to rotate without being in contact with the first grooved cam 6. (The two planetary gear trains do not have a fixed element and thus cannot transmit torque, but the handle for shifting passengers There is no rotational force input from the push rim since

At the same time, the guide groove 3a of the second groove cam, which rotates together with the guide groove of the first groove cam, decelerates the second groove cam 7 which is not rotated by the groove cam rotational direction fixing member 4. Guides to the position of 7 ^"'which engages with the inner circumference of the projection 9b. Therefore, the second groove cam 7 and the reduction gear 1 sun gear 9 mesh with each other, and the reduction gear 1 sun gear 9 is the central axis (1). At this time, the acceleration sun gear 8 is freely rotated because it is not in contact with the first groove cam or the second groove cam, and even when the reduction sun gear 9 is rotated, the entire projection of the main surface is engaged at a time. There is no friction noise or resistance due to coupling, so shifting is smooth.

When the rotational force is input from the push rim 16 in the state where the gear is shifted to the deceleration stage 1, the rotational force is transmitted to the three planetary gear shafts 19 via the input career 14. This rotational force is transmitted to the output career ring gear 12, the acceleration sun gear 8, and the deceleration two-stage sun gear 23 through the acceleration planetary gear 10, but without the fixed elements. The gear train is in an idling state, and is transmitted to the ring gear with an input career through the input career ring gear holder 15 coupled to the planetary gear shaft 19, and the first gear reduction gear 11 and the first gear reduction gear are decelerated. The transmission force is transmitted to the sun gear 9 so that only the deceleration stage 1 planetary gear train is operated and the rotational force is decelerated and transmitted to the output career 17a coupled to the deceleration stage 1 planetary gear shaft.

When the occupant selects the direct connection mode by operating the shift knob, the acceleration shifting line 36 is pulled and the reduction shifting line 35 is loosened, and thus the shifting strap 30 rotated on the wheel center shaft support rotates. The shifting sleeve integrally coupled with the shifting strap rotates counterclockwise to return to the direct connection position. The process of shifting from the deceleration stage 1 state to the direct connection state is the reverse of the process of shifting from the direct connection state to the deceleration stage 1 state.

FIG. 7 is a partial cross-sectional view illustrating a two-stage reduction mode of the four-speed double planetary gear type transmission of FIG. 1, and is a cross-sectional view taken along the line CC of FIG. 3.

When the rider selects the deceleration stage 2 mode by operating the shift knob in the deceleration stage 1, the deceleration shifting line 35 is pulled, and the acceleration shifting line 36 is loosened and installed on the wheel center shaft support 27 to rotate. The shift strap 30 rotates, and the shift sleeve 3 integrally coupled with the shift strap 27 rotates clockwise.

When the shift sleeve 3 rotates, the guide groove 3b of the first groove cam 6 decelerates the first groove cam 6 that is not rotated by the groove cam rotation direction fixing member 4, and the second stage sun gear 23 is rotated. ) Guides you to the 6 ^' position that engages with the protrusion. Therefore, the first home cam 6 and the deceleration two-stage sun gear 23 mesh with each other, and the deceleration two-stage sun gear 23 is fixed to the central axis 1.

At the same time, the guide groove 3a of the second groove cam, which rotates together with the guide groove of the first groove cam, is installed so that the second groove cam 7 is not rotated by the groove cam rotation direction fixing member 4, and the rotation sleeve 3 and the groove cam rotate. The acceleration sun gear 8 and the reduction gear 1 sun gear 9 are separated by the direction fixing member 4 and positioned at 7 ^" so as not to contact the two sun gears between the spaces 9b. (8) is not in contact with the first home cam or the second home cam, the deceleration first-stage sun gear 9 also does not contact the second home cam, respectively, is in the idle state.

When the rotational force is input from the push rim 16 in the state where the gear is shifted to the deceleration two-stage state, the rotational force is transmitted to the three planetary gear shafts 19 via the input career 14. This rotational force is transmitted to the output career ring gear 12 and the acceleration sun gear 8 and the reduction gear 2 sun gear 23 through the acceleration planetary gear 10, and only the reduction gear 2 of the planetary gear train fixed to the central axis is provided. The rotational force is decelerated and transmitted according to the transmission ratio determined to the output career 17a through the output career-attached ring gear 12 coupled to the deceleration two-stage planetary gear shaft.

The multi-speed planetary gearbox is configured to have a different diameter by reducing the two-speed planetary gear to the reduction gear 1 gear located in the reduction gear row, unlike the double-speed planetary gearbox described above. Therefore, the two-speed reduction gear is also located in the reduction gear row, and accordingly, the cam groove of the transmission sleeve needs to be appropriately changed.

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, the career serves as the housing of the transmission, so it is small and light, and the central shaft can be attached to or detached from the vehicle body, and a planetary gear type transmission having four or more shifting capacities without using a clutch is provided.

In particular, when applied to the wheels of a wheelchair, the passenger can shift at a low speed to easily climb a hill or drive on a sand or carpet with a small force, and to travel at a high speed by shifting at a high speed.

Claims (9)

By combining two single planetary gear trains, one career and the other ring gear are integrated, and the two careers, which are divided into the input side and the output side, cooperate to form a housing of the transmission, and can rotate on a fixed central axis. In the planetary gear transmission for shifting by combining or separating each of the installed sun gears to the central axis, and controlling the integration or separation of the adjacent sun gear, At least one planetary gear is installed in each career; at least one of the planetary gears; and three or more sun gears engaged with respective stages of the planetary gears and having a plurality of concave portions formed on the inner circumferential surface for coupling with the central axis. Features planetary gearbox According to claim 1, The composite planetary gear installed in the career 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, the plurality of other A planetary gearbox further comprising a sun gear meshing with the planetary gear The planetary gear of claim 1, wherein the planetary gears installed in the career further include a plurality of planetary gears included in a simple planetary gear train, and other planetary gears having different diameters based on the planetary gears. Planetary gearbox further comprising interlocking sun gear The apparatus of claim 1, wherein the mechanism for coupling or separating each sun gear with the central axis, and for integrating or separating the two sun gears, 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 groove cam rotational direction fixing member fixed to the central shaft and having at least one guide groove which encloses the shift sleeve and is elongated in the axial direction; 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; 5. The method of claim 4, wherein the two sun gears having concave-convex portions on opposite sides and the two sun gears are pressed in the axial direction by the home cam in a state in which all the sun gears in the transmission are not fixed to the central axis. The planetary gear type transmission further comprises an elastic member between the two sun gears so that the two sun gears operate as one and the two sun gears operate as one, and do not engage with each other when the axial pressure is released. The method of claim 4, 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 According to claim 5 to 6, 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. A groove that is inclined toward the groove and a cam groove continuously guiding to a position where the two sun gears do not engage with each other; Planetary gear type transmission characterized in that formed; The planetary gear transmission according to claim 4, wherein the home cam is inserted into the guide groove. The planetary gear type transmission according to claim 4, wherein the home cam has a convex portion for engaging with the recess of the sun gear.

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