KR20090090095A - High gear ratio gearbox that use epicyclic gear - Google Patents

High gear ratio gearbox that use epicyclic gear Download PDF

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Publication number
KR20090090095A
KR20090090095A KR1020080015362A KR20080015362A KR20090090095A KR 20090090095 A KR20090090095 A KR 20090090095A KR 1020080015362 A KR1020080015362 A KR 1020080015362A KR 20080015362 A KR20080015362 A KR 20080015362A KR 20090090095 A KR20090090095 A KR 20090090095A
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South Korea
Prior art keywords
gear
rotated
sun gear
planetary gear
input shaft
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KR1020080015362A
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Korean (ko)
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이명희
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이명희
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Priority to KR1020080015362A priority Critical patent/KR20090090095A/en
Publication of KR20090090095A publication Critical patent/KR20090090095A/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02095—Measures for reducing number of parts or components

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a high speed transmission apparatus using planetary gear trains, and includes a first sun gear fixed to an input shaft, a first planetary gear installed in a housing so as to engage and rotate with a first sun gear, and a first ring gear engaged with a first planetary gear. A reverse planetary gear array consisting of a second planetary gear connected to the input shaft and a second planetary gear connected to the input shaft, a second planetary gear installed on the carrier to rotate and rotate, and a second planetary gear engaged with the second planetary gear and rotated in connection with the first ring gear Forward planetary gears made of ring gears are combined with each other.

Therefore, in the present invention, the rotational power supplied from the input shaft is decelerated by the forward planetary gear sequence and then again by the second ring gear reversely rotated by the reverse planetary gear sequence. Therefore, high speed reduction is achieved while the rotational power of the input shaft is transmitted to the reverse planetary gear sequence and forward planetary gear sequence, and then through the carrier to the output shaft. Therefore, the transmission ratio is significantly reduced compared to the prior art while minimizing the overall size and the number of parts. May be augmented.

Description

High gear ratio gearbox that use epicyclic gear

The present invention relates to a high transmission using a planetary gear, and more particularly to a high transmission using a planetary gear that can obtain a high speed ratio or a high speed reduction ratio.

The transmission is a device that changes the rotational speed or rotational force in a motor such as a car. This gearbox is composed of gears having different teeth, and the gear ratio of the gears of the two gears is increased, the greater the deceleration or increase in speed, and the smaller the gear ratio of the gears of the two gears, the smaller the gear ratio. Shift is made.

1 is a schematic diagram showing a conventional transmission structure using a small gear connected to an input stage and a relatively large gear connected to an output stage to obtain a high reduction ratio or a high reduction ratio.

When the gear teeth of a1 are 14, the gear teeth of a2 is 112, and the rotation speed of the input stage is 100, the gear ratio is a2 / a1 and the rotation speed of the output stage is 100 / (a2 / a1). Therefore, the gear ratio is 112/14 = 8, and the output speed is 100 / (112/14) = 12.5.

This conventional transmission requires a small gear, such as a1, and a relatively large gear, such as a2, to significantly decelerate 100 revolutions to 12.5 revolutions or to greatly speed up 12.5 revolutions to 100 revolutions. Therefore, such a conventional transmission must have a relatively large gear in order to obtain a high speed ratio or a high speed reduction ratio, and accordingly, there is a problem in that the overall size of the speed change is greatly increased.

FIG. 2 is a schematic view showing an embodiment of a conventional transmission device that solves the problems of FIG. 1, which may achieve high speed or high speed by using relatively small gears instead of a large gear as shown in FIG. 1.

That is, when the gear teeth of b1, b3, b5 are 14, the gear teeth of b2, b4, b6 are 28, and the rotation speed of the input stage is 100, the gear ratio is (b2 / b1) × (b4 / b3) × (b6 / b5), and the rotation speed of the output stage is 100 / ((b2 / b1) × (b4 / b3) × (b6 / b5)). Therefore, the gear ratio is (28/14) × (28/14) × (28/14) = 8, and the rotation speed of the output stage is 100 / ((28/14) × (28/14) × (28/14)) = 12.5.

The transmission of FIG. 2 is equipped with several pairs of gears and a plurality of shafts to decelerate 100 revolutions to 12.5 revolutions or to speed up 12.5 revolutions to 100 revolutions. Therefore, the transmission of FIG. 2 has the advantage of reducing the overall size of the product because the desired transmission ratio can be obtained even if the size of the gear is not larger than that of FIG. 1, but a large number of gears and shafts are provided to obtain a large transmission ratio. Since the number of parts has to be increased, the unit cost and assembly labor of the product are increased.

SUMMARY OF THE INVENTION An object of the present invention for solving the above problems is to provide a high transmission using planetary gears to obtain a high reduction ratio or a high reduction ratio with a relatively simple configuration.

High transmission device using the planetary gear of the present invention for achieving the above object, the input shaft is installed to rotate in the center of the housing; A first sun gear fixed to the circumference of the input shaft and rotated therewith; First planetary gears radially engaged around the first sun gear and whose centers are installed in the housing to rotate in the opposite direction when the first sun gear rotates; A first ring gear installed on the inner circumferential surface so that the first planetary gears are engaged and the outer circumferential surface is rotated on the inner circumferential surface of the housing and rotated in the opposite direction when the first sun gear rotates; A second sun gear connected to the first sun gear and rotated therewith; Second planetary gears radially engaged around the second sun gear, the centers of each of which are installed to rotate, and the entirety of the second planetary gears to revolve about the second sun gear; A second ring gear connected to the first ring gear and rotated therewith and the second planetary gears mesh with the inner circumferential surface; A carrier which is installed to rotate each of the second planetary gears and rotates along the revolution direction when the second planetary gears revolve about the second sun gear; And an output shaft fixed to the carrier and rotated therewith.

As described above, the present invention includes a first planetary gear fixed to an input shaft, a reverse planetary gear array including a first planetary gear installed in a housing and a first ring gear engaged with a first planetary gear so as to engage and rotate with the first sun gear, Forward direction consisting of a second sun gear connected to the input shaft, a second planetary gear installed on the carrier so as to rotate and revolve with the second sun gear, and a second ring gear that is engaged with the second planetary gear and is connected to the first ring gear and rotates with it. Planetary gears are combined with each other. Therefore, while the rotational power supplied from the input shaft is transmitted to the reverse planetary gear sequence and forward to the output planetary gear sequence, and is transmitted to the output shaft through the carrier, it is highly decelerated, and it is accelerated if the input / output is interchanged, thereby minimizing the total size and the number of parts of the transmission. At the same time, the speed ratio can be greatly increased compared to the conventional art.

Specific features and advantages of the present invention will become more apparent from the following description taken in conjunction with the accompanying drawings.

3 and 4 are cross-sectional views and schematic views showing an embodiment of the high speed shift apparatus using the planetary gear of the present invention, and FIG. 5 is a schematic view showing a power transmission relationship of the reverse planetary gear array 2, and FIG. It is a schematic diagram which shows the power transmission relationship of the forward planetary gear row 5.

This is installed in the center of the housing 4 so that the input shaft 1 is rotated in the direction of the arrow a. The first sun gear Z1 is fixed around the input shaft 1 so as to rotate in the direction of the arrow b. A plurality of first planetary gears Z2 are radially engaged around the first sun gear Z1 to rotate in the direction of the arrow c. One end of the first planetary gear shaft 3 is provided at the center of the first planetary gears Z2, and the other end of the first planetary gear shaft 3 is fixed to the housing 4. Therefore, the first planetary gears Z2 do not revolve around the first sun gear Z1, but rotate only about the first planetary gear axis 3. Therefore, the first planetary gears Z2 are rotated in the opposite directions about the first planetary gear shaft 3 when the first sun gear Z1 is rotated.

The inner circumferential surface of the first ring gear Z3 is meshed around the first planetary gears Z2, and the outer circumferential surface of the first ring gear Z3 is rotated in the direction of arrow d on the inner circumferential surface of the housing 4. It is installed. Therefore, when the first sun gear Z1 is rotated in the direction of the arrow b, the first sun gear Z1 is rotated in the reverse direction d of the first sun gear Z1 by the first planetary gears Z2 which are reversely rotated in the direction of the arrow c.

Here, the first sun gear Z1, the first planetary gears Z2, and the first ring gear Z3 form a reverse planetary gear array 2 of the high speed transmission apparatus of the present invention, and the reverse planetary gear array 2 ) Serves to switch the direction of rotation transmitted from the input shaft 1 in the reverse direction and to decelerate.

On the other hand, one side of the input shaft 1 is connected to the second sun gear (Z4), and thus, when the input shaft 1 is rotated in the direction of the arrow (e) together with the first sun gear (Z1). A plurality of second planetary gears Z5 are radially engaged around the second sun gear Z4. One end of the second planetary gear shaft 6 is provided at the center of the second planetary gears Z5, and the other end of the second planetary gear shaft 6 is fixed to the carrier 7. Accordingly, the second planetary gears Z5 rotate in the direction of the arrow f about the second planetary gear shaft 6 when the second sun gear Z4 rotates, and the arrow g is centered on the second sun gear Z4. Direction and thus, the carrier 7 fixed to the second planetary gear shaft 6 is rotated about the second sun gear Z4 in the direction of the arrow g.

The inner circumferential surface of the second ring gear Z6 is engaged around the second planetary gears Z5. The second ring gear Z6 is connected to the first ring gear Z3. Accordingly, when the first ring gear Z3 is rotated in the direction of the arrow d, the second ring gear Z6 is rotated in the direction of the arrow i. do.

Here, the second sun gear Z4, the second planetary gears Z5, and the second ring gear Z6 form a forward planetary gear array 5 of the high speed transmission apparatus of the present invention. The forward planetary gear sequence 5 serves to transmit the power of the input shaft 1 to the output shaft 8 and to reduce the rotational direction of the power transmission shaft so as not to change.

The second planetary gear shafts 6 are radially fixed to the carrier 7, and the output shaft 8 is fixed to the center thereof. Accordingly, the second planetary gears Z5 around the second sun gear Z4 are rotated in the direction of the arrow f about the second planetary gear axis 6, and the arrow g direction is centered on the second sun gear Z4. When it rotates, the carrier 7 and the output shaft 8 fixed thereto are rotated in the direction of the arrow g (h).

Reference numeral 9 is a cover that opens and closes the opening of the housing 4 and is supported to rotate the output shaft 8.

In the high speed transmission apparatus using the present invention planetary gear train having such a configuration, the reverse planetary gear train 2 and the forward planetary gear train 5 are combined with each other. The reverse planetary gear array 2 has a first planetary gear Z1 fixed to the input shaft 1, a first planetary gear Z2 installed in the housing 4 so as to engage and rotate with the first sun gear Z1, and a first planetary planetary gear. The first ring gear Z3 meshes with the gear Z2. The reverse planetary gear sequence 2 reverses the first ring gear Z3 and decelerates greatly.

The forward planetary gear array 5 includes a second sun gear Z4 fixed to the input shaft 1, a second planetary gear Z5 installed on the carrier 7 so as to engage and rotate and revolve with the second sun gear Z4. It consists of a second ring gear Z6 meshed with the planetary gear Z5 and fixed to the first ring gear Z3 and rotated therewith. The forward planetary gear array 5 includes an output shaft 8 having an input shaft 1. It rotates in the same forward direction as) and greatly reduces the rotational speed of the output shaft (8).

On the other hand, the second ring gear Z6 is reversely rotated in the direction of the arrow i by the first ring gear Z3, which is the reverse planetary gear array 2, while the second planetary gears Z5 are forward planetary gears. The row 5 rotates forward along the inner circumferential surface of the second ring gear Z6 in the direction of the arrow g. Therefore, the revolution speed of the forward direction g of the second planetary gears Z5 is made along the inner circumferential surface of the second ring gear Z6 that is reversely rotated.

In the present invention, the rotational power supplied from the input shaft 1 is decelerated by the forward planetary gear sequence 5 and then again by the second ring gear Z6 that is reversely rotated by the reverse planetary gear sequence 2. Slows down. Therefore, since the rotational power of the input shaft 1 is transmitted to the reverse planetary gear sequence 2 and is transmitted to the forward planetary gear sequence 5 and then transmitted to the output shaft 8 through the carrier 7, the speed change is performed. The transmission ratio can be greatly increased as compared to the related art while minimizing the overall size and the number of parts of the device.

Referring to the operation and effects of the high transmission using the planetary gear sequence of the present invention by substituting specific numerical values as follows.

The number of rotations of the input shaft 1 is 100, the number of teeth of the gear is respectively 1st sun gear Z1 = 14, 1st ring gear Z3 = 58, 2nd sun gear Z4 = 19, 2nd ring gear Z6 = 58,

(1) Since the gear ratio of the reverse planetary gear array 2 is Z3 / Z1, 58/14 = 4.142857.

(2) Since the rotational speed by the reverse planetary gear sequence 2 is 100 / (Z3 / Z1), 100 / 4.142857 = 24.13793. Therefore, when the input shaft 1 rotates 100 times, the first ring gear Z3 of the reverse planetary gear sequence 2 rotates 24.13793 in the opposite direction. Here, since the second ring gear Z6 of the forward planetary gear sequence 5 is fixed to the first ring gear Z3, the first ring gear Z3 rotates in the opposite direction to the input shaft 1 by 24.13793. In the same direction as the first ring gear Z3, it rotates by 24.13793.

The reverse rotation of the second ring gear Z6 reduces the idle speed of the second planetary gears Z5. That is, the second planetary gears Z5 revolve around the second sun gear Z4 while being engaged with the inner circumferential surface of the second ring gear Z6. Since the second ring gear Z6 itself rotates in reverse, its inner circumferential surface The revolving speed of the second planetary gears Z5 meshed with is reduced by that amount.

If the rotational speed of the forward planetary gear sequence 5, that is, the revolution speed of the second planetary gears Z5 and the reverse rotational speed of the second ring gear Z6 is the same, the output shaft 8 is stopped and the second planetary gear If the idle speed of the Z5 is faster than the reverse rotation speed of the second ring gear Z6, the output shaft 8 is decelerated and rotated in the same rotational direction as the input shaft 1, and the idle speed of the second planetary gears Z5 is increased. If the second ring gear Z6 is slower than the reverse rotation speed, the output shaft 8 is decelerated and rotated in the opposite direction to the input shaft 1.

(3) Since the gear ratio of the forward planetary gear array 5 is (Z6 / Z4) +1, (58/19) +1 = 4.05263.

(4) Since the number of revolutions by the forward planetary gear sequence 5 is 100 / ((Z6 / Z4) +1), 100 / 4.05263 = 24.67533.

(5) Since the rotational speed of the output shaft 8 is the rotational speed by the forward planetary gear sequence 5-the rotational speed by the reverse planetary gear sequence 2, 100 / ((Z6 / Z4) +1)-100 / (Z3 / Z1). That is, 24.67533-24.13793 = 0.5374.

Therefore, when the rotation speed of the input shaft 1 is 100, the rotation speed of the output shaft 8 is 0.5374, and the deceleration degree is very large.

Here, as described above, when the value of the rotational speed of the output shaft 8 is positive (+), the output shaft 8 is rotated in the same direction as the rotational direction of the input shaft 1. When the value of the rotational speed of the output shaft 8 is negative, the output shaft 8 is rotated in the direction opposite to the rotational direction of the input shaft 1.

(6) The gear ratio of the high speed transmission apparatus of the present invention is 100 / (100 / ((Z6 / Z4) +1)-100 / (Z3 / Z1)), so 100 / 0.5374 = 186. Therefore, the reduction gear ratio of the high transmission using the planetary gear array of the present invention is 186 when the above gear teeth are applied.

The reduction gear ratio of the high speed transmission apparatus of the present invention is formulated as follows. That is, reduction gear ratio = (Z3 x (Z4 + Z6)) / (Z3 x Z4- (Z1 x (Z4 + Z6)).

In the present invention, the rotational speed of the input shaft 1 is decelerated once by the forward planetary gear sequence 5, and again by the second ring gear Z6 reversely rotated by the reverse planetary gear sequence 2. Decelerates once. That is, the revolving speed of the second planetary gears Z5 is further reduced due to the reverse rotation of the second ring gear Z6. The second planetary gears Z5 revolve around the second sun gear Z4 while being engaged with the inner circumferential surface of the second ring gear Z6. Since the second ring gear Z6 itself rotates in reverse, the second ring gear The forward idle number of the second planetary gear Z5 is reduced by the reverse rotation speed of Z6. Therefore, the output shaft 8 is decelerated once by the forward planetary gear sequence 5 and decelerated once more by the second ring gear Z6 which is reversely rotated by the reverse planetary gear sequence 2 and thus high deceleration.

Here, when the rotational speed by the forward planetary gear sequence 5 is less than 100 / (Z3 / Z1), the rotation direction of the output shaft 8 is rotated opposite to the rotation direction of the input shaft 1, and the forward planetary gear sequence 5 is performed. When the rotational speed by is greater than 100 / (Z3 / Z1), the rotation of the output shaft 8 rotates in the same direction as the rotational direction of the input shaft 1, and the rotational speed by the forward planetary gear sequence 5 is 100 / ( If it is equal to Z3 / Z1), the output shaft 8 is in a stopped state.

On the other hand, in the case where the high transmission using the planetary gear sequence of the present invention is used as the high speed increasing device, the rotational power may be input to the output shaft 8 to be output to the input shaft 1. In this case, the principles described with reference to FIGS. 3 to 6 may be reversely applied to obtain a significantly increased rotation speed compared to the input rotation speed.

7 is a schematic view showing another embodiment of the high transmission using the planetary gear array of the present invention, which is fixed around the input shaft 11 and the input shaft 11 installed to rotate in the center of the housing 14. The first sun gear Z1 rotated together with the first sun gear Z1, and radially meshed around the first sun gear Z1. The centers of the first sun gear Z1 are rotated in the opposite direction when the first sun gear Z1 rotates. The first planetary gear Z2 and the first planetary gear Z2 are meshed with the inner circumferential surface, and the outer circumferential surface is installed to rotate on the inner circumferential surface of the housing, and rotates in the opposite direction when the first sun gear Z1 is rotated. (Z3), the second sun gear (Z4) is provided on one side of the first sun gear (Z1) and fixed to the circumference of the input shaft 11 and rotated together with the second sun gear (Z4) radially Each center is installed to rotate and the whole is revolved around the second sun gear Z4. The second planetary gears Z5 installed to be installed, the second ring gears Z6 fixed to the first ring gear Z3, rotated therewith, and the second planetary gears Z5 joined to the inner circumferential surface thereof, respectively, When the second planetary gears Z5 are installed to rotate and the second planetary gears Z5 revolve around the second sun gear Z4, the carriers 17 and the carriers 17 rotate along the revolution direction thereof. A drive gear 19 fixed and rotated together with the drive gear 19, an electric gear 20 that is engaged with the drive gear 19 and rotates when driven, and an output shaft 18 that is fixed to the drive gear 20 and rotates with it. Is done.

The present invention exchanges the positions of the forward planetary gear sequence 15 and the reverse planetary gear sequence 12, and the drive gear 19 and the electric gear 20 between the forward planetary gear sequence 15 and the output shaft 18. It is installed form. Due to this configuration change, the position of the output shaft 18 can be changed relatively freely, and the output shaft 18 can be positioned parallel to this on one side of the input shaft 11. Since the remaining operations and effects of the high speed shift apparatus using the planetary gear array of the present invention are the same as those described with reference to FIGS. 3 to 6, redundant description thereof will be omitted.

8 is a schematic view showing another embodiment of the high speed shift apparatus using the planetary gear array of the present invention, which includes an input shaft 21 and a drive gear 29 fixed to the input shaft 21 and rotated together with the input shaft 21. The first gear (Z1) and the first sun gear (Z1), which are engaged with the drive gear (29) and rotated at the time of driving thereof, are fixed to the electric gear (30) and rotated together with the drive gear (29). The first planetary gears Z2, which are radially engaged and whose centers are installed in the housing 24 and rotate in the opposite direction when the first sun gear Z1 rotates, and the first planetary gears Z2 are joined to the inner circumferential surface thereof. The outer circumferential surface is installed to rotate on the inner circumferential surface of the housing 24 and is fixed to one side of the first ring gear Z3 and the first sun gear Z1 which rotates in the opposite direction when the first sun gear Z1 is rotated, and rotates with it. Radially meshed around the second sun gear Z4 and the second sun gear Z4, and the centers of the second sun gear Z4 are rotated. The second planetary gears Z5 and the first planetary gears Z5, which are installed so as to revolve around the second sun gear Z4 and the first ring gear Z3, are rotated together with the second planetary gear ( When the second ring gear Z6 into which the Z5 meshes and the second planetary gear Z5 rotate to rotate, and the second planetary gear Z5 revolves around the second sun gear Z4, The carrier 27 is rotated along the direction, and the output shaft 28 is fixed to the carrier 27 and rotated with it.

In the present invention, the drive gear 29 and the electric gear 30 is provided on the input shaft 21, and the rotational power of the electric gear 30 is transmitted to the reverse planetary gear sequence 22 and the forward planetary gear sequence 25. It is supposed to be. The electric gear 30, the first sun gear Z1, and the second sun gear Z4 are connected by the hollow shaft 31 to enable the power transmission. The output shaft 28 is positioned to pass through the inside of the hollow shaft 31, and one end of the output shaft 28 is connected to the forward planetary gear array 25.

The present invention described above has an advantage that the position of the input shaft 21 can be freely changed in the state where the output shaft 28 is located at the center of the high speed transmission apparatus of the present invention, and the input shaft 21 has one side of the output shaft 28. In parallel to it. Since the remaining operations and effects of the high speed shift apparatus using the planetary gear array of the present invention are the same as those described with reference to FIGS. 3 to 6, redundant description thereof will be omitted.

1 is a schematic view showing an embodiment of a conventional transmission;

Figure 2 is a schematic diagram showing another embodiment of the conventional transmission

3 and 4 is a cross-sectional view showing an embodiment of a high transmission using the planetary gear of the present invention and a schematic view thereof

Figure 5 is a schematic diagram showing the power transmission relationship of the reverse planetary gear sequence

6 is a schematic view showing a power transmission relationship of the forward planetary gear sequence;

Figure 7 is a schematic diagram showing another embodiment of the high transmission using the planetary gear of the present invention

8 is a schematic view showing another embodiment of the high speed shift apparatus using the planetary gear according to the present invention.

* Description of the symbols for the main parts of the drawings *

1,11,21: Input shaft 2,12,22: Reverse planetary gear sequence

3, 13, 23: first planetary gear shaft 4, 14, 24: housing

5,15,25: Forward planetary gear array 6,16,26: Second planetary gear shaft

7,17,27: carrier 8,18,28: output shaft

9: Cover 19,29: Drive Gear

20,30: Electric gear 31: Hollow shaft

Z1: First Sun Gear Z2: First Planetary Gear

Z3: First ring gear Z4: Second sun gear

Z5: Second planetary gear Z6: Second ring gear

Claims (3)

An input shaft 1 that receives rotational power from the outside; A first sun gear Z1 fixed to the circumference of the input shaft 1 and rotated therewith; Radially engaged around the first sun gear Z1 and the centers thereof are installed so as not to be interlocked with the rotation of the input shaft 1 in the housing 4 so as to rotate in the opposite direction when the first sun gear Z1 is rotated. First planetary gears Z2; A first ring gear (Z3) which is installed so that the first planetary gears (Z2) are engaged with the inner circumferential surface and the outer circumferential surface is rotated on the inner circumferential surface of the housing (4) and rotated in the opposite direction when the first sun gear (Z1) is rotated; A second sun gear Z4 provided at one side of the first sun gear Z1 and connected to the input shaft 1 to rotate together; Second planetary gears (Z5) radially engaged around the second sun gear (Z4) and installed so that their respective centers are rotated, and the whole of them are revolved about the second sun gear (Z4); A second ring gear (Z6) rotated in association with the first ring gear (Z3) and the second planetary gears (Z5) mesh with the inner circumferential surface; A carrier 7 installed to rotate each of the second planetary gears Z5 and being rotated along the revolution direction when the second planetary gears Z5 revolve around the second sun gear Z4; An output shaft (8) fixed to the carrier (7) is rotated with it; high transmission using planetary gears, characterized in that consisting of. Input shaft 11; A first sun gear Z1 fixed around the input shaft 11 and rotated therewith; Radially engaged around the first sun gear Z1 and the centers thereof are installed so as not to be interlocked with the rotation of the input shaft 11 in the housing 14 to rotate in the opposite direction when the first sun gear Z1 is rotated. First planetary gears Z2; A first ring gear (Z3) that is engaged with the first planetary gear (Z2) on an inner circumferential surface and installed so that the outer circumferential surface is rotated on the inner circumferential surface of the housing and rotates in the opposite direction when the first sun gear (Z1) is rotated; A second sun gear Z4 provided at one side of the first sun gear Z1 and connected to the input shaft 11 to rotate together; Second planetary gears (Z5) radially engaged around the second sun gear (Z4) and installed so that their respective centers are rotated, and the whole of them are revolved about the second sun gear (Z4); A second ring gear (Z6) interlocked with the first ring gear (Z3) and rotated therewith and the second planetary gears (Z5) mesh with an inner circumferential surface thereof; A carrier (17) which is installed so that each of the second planetary gears (Z5) is rotated and the second planetary gears (Z5) are rotated along the revolution direction when the second planetary gears (Z5) revolve around the second sun gear (Z4); A drive gear 19 fixed to the carrier 17 and rotating together with it; An electric gear 20 that is engaged with the drive gear 19 and rotates when driven; Fixed to the electric gear 20, the output shaft 18 is rotated with it; High transmission using a planetary gear, characterized in that consisting of. Input shaft 21; A drive gear 29 fixed to the input shaft 21 and rotated therewith; An electric gear 30 meshed with the drive gear 29 and having a hollow hollow shaft 31 having a hollow central portion thereof which is rotated when driven; A first sun gear Z1 fixed to the electric gear 30 and rotated therewith; The first planetary gear is radially engaged around the first sun gear Z1 and the center thereof is installed in the housing 24 so as not to be interlocked with the rotation of the input shaft. Gears Z2; A first ring gear (Z3) which is installed to engage the first planetary gear (Z2) on an inner circumference and rotates on an inner circumference of the housing (24) and rotates in the opposite direction when the first sun gear (Z1) is rotated; A second sun gear Z4 connected to one side of the first sun gear Z1 and rotated therewith; Second planetary gears Z5 radially engaged around the second sun gear Z4 and installed so that their respective centers are rotated, and the whole of them are revolved about the second sun gear Z4; A second ring gear (Z6) interlocked with the first ring gear (Z3) and rotated therewith and the second planetary gears (Z5) mesh with an inner circumferential surface thereof; A carrier 27 installed to rotate each of the second planetary gears Z5 and being rotated along the revolution direction when the second planetary gears Z5 revolve around the second sun gear Z4; The high speed transmission using planetary gears, characterized in that the output shaft 28 is fixed to the carrier 27 and rotated together with the output shaft 28 is passed through the inside of the hollow shaft (31).
KR1020080015362A 2008-02-20 2008-02-20 High gear ratio gearbox that use epicyclic gear KR20090090095A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011129554A2 (en) * 2010-04-13 2011-10-20 Lee Myung Hee High-efficiency continuously variable transmission
KR101654501B1 (en) * 2016-02-03 2016-09-05 류금모 Planetary reduction gear
CN110864085A (en) * 2019-11-20 2020-03-06 张晓佳 Speed reducer

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011129554A2 (en) * 2010-04-13 2011-10-20 Lee Myung Hee High-efficiency continuously variable transmission
WO2011129554A3 (en) * 2010-04-13 2011-12-29 Lee Myung Hee High-efficiency continuously variable transmission
KR101654501B1 (en) * 2016-02-03 2016-09-05 류금모 Planetary reduction gear
CN110864085A (en) * 2019-11-20 2020-03-06 张晓佳 Speed reducer

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