KR101779103B1 - Planetary gear train - Google Patents

Planetary gear train Download PDF

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KR101779103B1
KR101779103B1 KR1020150119563A KR20150119563A KR101779103B1 KR 101779103 B1 KR101779103 B1 KR 101779103B1 KR 1020150119563 A KR1020150119563 A KR 1020150119563A KR 20150119563 A KR20150119563 A KR 20150119563A KR 101779103 B1 KR101779103 B1 KR 101779103B1
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gear
pinion
teeth
output
gears
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KR1020150119563A
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KR20170024381A (en
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제환영
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유피모터주식회사
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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
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital gears

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

A planetary gear train according to a first embodiment of the present invention includes: a planetary carrier including a plurality of double gears of two pinion gears; A stationary ring gear that is gear-coupled to the outside of any one of the two pinion gears; An output ring gear that is gear-coupled to the outside of the other one of the two pinion gears; And an input line gear which meshes with an inside of the pinion gear of any one of the two pinion gears.
In the planetary gear train of the present invention, the number of teeth of the output ring gear and the number of teeth of the output ring gear, which are provided on the same axis as the fixed pinion gear, when the fixed pinion gear that is gear- And the output ring gear is further rotated or rotated by the difference in the number of teeth through which the output pinion gear is gear-engaged, thereby realizing a large gear ratio.

Description

[0001] PLANETARY GEAR TRAIN [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear train, and more particularly, to a planetary gear train having a simple structure and capable of implementing a large gear ratio.

Generally, in order to obtain a high gear ratio through the planetary gear train, it is difficult to manufacture the planetary gear train in a multi-stage structure.

Therefore, in order to realize a gear train having a high gear ratio, a harmonic drive may be used. A typical harmonic drive consists of a wave generator, a flexible spline, and a circular spline.

This harmonic drive has a simple structure like a planetary gear train but can achieve a high gear ratio. In addition, the harmonic drive has a small size compared to a high gear ratio and has no backlash. Since the flexible spline and the circular spline are meshed at only two places, the noise reduction is low and the transmission efficiency is high when the rotation speed is low .

However, it is very difficult to manufacture a flexible spline that can withstand frequent deformation, and when the rotation speed is high, the frictional force generated between the wave generator and the flexible spline is large, so that the transmission efficiency is low. Further, when the gear ratio is small, since the deformation of the flexible spline is large, there arises a problem that a large rotational force is required to drive the gear.

Therefore, the demand for a planetary gear train capable of realizing a high gear ratio is continuously increasing.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a planetary gear train capable of realizing a high gear ratio.

According to a first aspect of the present invention, there is provided a planetary gear train including: a planetary carrier including a plurality of double gears of two pinion gears; A stationary ring gear that is gear-coupled to the outside of any one of the two pinion gears; An output ring gear that is gear-coupled to the outside of the other one of the two pinion gears; And an input line gear which meshes with an inside of the pinion gear of any one of the two pinion gears.

The gear ratio of the planetary gear train according to the first embodiment of the present invention is

Figure 112015082421524-pat00001

. ≪ / RTI >

When three double gears are provided, the number of teeth of the input line gear is formed to be a multiple of three, and the number of teeth of the ring gear that is gear-coupled with the pinion gear that is gear-coupled with the input line gear may be a multiple of three.

When four double gears are provided, the number of teeth of the input line gear is an even number, and the number of teeth of the ring gear that is gear-coupled with the pinion gear that is gear-coupled with the input line gear may be an even number.

A planetary gear train according to a second embodiment of the present invention includes: a planetary carrier including a plurality of triple-gears including a fixed pinion gear, an output pinion gear, and an input pinion gear; A stationary ring gear that is gear-engaged outside the stationary pinion gear; An output ring gear that is gear-engaged outside the output pinion gear; And an input line gear that gears in the inside of the input pinion gear.

The gear ratio of the planetary gear train according to the second embodiment of the present invention is

Figure 112015082421524-pat00002

. ≪ / RTI >

A planetary gear train according to a third embodiment of the present invention includes: a planetary carrier including a plurality of triple gears including a fixed pinion gear, an output pinion gear, and an input pinion gear; A fixed line gear that is gear-engaged inside the fixed pinion gear; An output line gear that meshes with the inside of the output pinion gear; And an input line gear that gears in the inside of the input pinion gear.

The gear ratio of the planetary gear train according to the third embodiment of the present invention is

Figure 112015082421524-pat00003
. ≪ / RTI >

According to the planetary gear train of the present invention as described above, it is possible to realize a planetary gear train having a simple structure and being easy to manufacture and having a large gear ratio through a planetary carrier composed of a double gear or a triple gear.

These drawings are for the purpose of describing an exemplary embodiment of the present invention, and therefore the technical idea of the present invention should not be construed as being limited to the accompanying drawings.
1 is an exploded perspective view showing a planetary gear train according to a first embodiment of the present invention.
2 is a perspective view showing a double gear of the planetary gear train according to the first embodiment of the present invention.
3 is an exploded perspective view showing a coupling relationship between the double gear and the ring gear of the planetary gear train according to the first embodiment of the present invention.
4 is a perspective view showing a planetary gear train according to a first embodiment of the present invention.
5 is a plan view showing a planetary gear train having three double gears according to a first embodiment of the present invention.
6 is a plan view showing a planetary gear train having four double gears according to a first embodiment of the present invention.
7 is a perspective view showing a planetary gear train according to a second embodiment of the present invention.
8 is a perspective view showing a triple gear of the planetary gear train according to the second and third embodiments of the present invention.
9 is a perspective view showing a planetary gear train according to a third embodiment of the present invention.
10 is an exploded perspective view showing a coupling relationship between a triple gear and a sun gear according to a third embodiment of the present invention.
11 is an exploded perspective view showing a coupling relationship between a triple gear and a sun gear according to a third embodiment of the present invention.
12 to 14 are views showing a process of assembling the planetary gear train according to the first embodiment of the present invention.
15 to 18 are views showing a process of assembling the planetary gear train according to the third embodiment of the present invention.

The present invention will be described in detail with reference to the accompanying drawings in order to facilitate a person skilled in the art to which the present invention pertains to the first embodiment of the present invention. The present invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein.

In order to clearly illustrate the present invention, parts not related to the description are omitted, and the same or similar components are denoted by the same reference numerals throughout the specification.

It is to be understood that both the foregoing general description and the following detailed description of the present invention are exemplary and explanatory and are intended to provide further explanation of the invention as claimed. .

Hereinafter, a planetary gear train according to a first embodiment of the present invention will be described in detail with reference to the accompanying drawings.

1 is an exploded perspective view showing a planetary gear train according to a first embodiment of the present invention. 2 is a perspective view showing the double gear 21 of the planetary gear train according to the first embodiment of the present invention. 3 is an exploded perspective view showing the coupling relationship of the double gear 21 and the ring gear of the planetary gear train according to the first embodiment of the present invention. 4 is a perspective view showing a planetary gear train according to a first embodiment of the present invention.

1 to 4, the planetary gear train according to the first embodiment of the present invention includes a planetary carrier 20 including a plurality of double gears 21 made up of two pinion gears, An output ring gear (33) gear-coupled to the outside of the other one of the two pinion gears, and a pinion gear And an input sun gear 10 that meshes with one of the pinion gears.

The double gear 21 is provided with the fixed pinion gear 22 and the output pinion gear 23 on the same axis. It is preferable that three or four double gears 21 are provided on the planetary carrier 20.

The fixed ring gear 32 is gear-engaged to the outside of the plurality of fixed pinion gears 22 and the output ring gear 33 is gear-connected to the outside of the plurality of output pinion gears 23.

The input sun gear 10 is gear-meshed inside the plurality of fixed pinion gears 22 or the output pinion gears 23.

The planetary gear train according to the first embodiment of the present invention is configured such that the fixed pinion gear 22 constituting the double gear 21 provided in the planetary carrier 20 is fixedly engaged with the fixed ring gear 22 meshing with the fixed pinion gear 22, The number of teeth of the output ring gear 33 and the number of teeth of the output pinion gear 23 rotating at the same rotational speed as that of the fixed pinion gear 22, .

That is, when the fixed pinion gear 22 that is gear-engaged with the fixed ring gear 32 rotates around the fixed ring gear 32, the output pinion gear 23 rotates the number of teeth of the fixed ring gear 32 And the number of teeth of the output pinion gear 23 is multiplied by the number of rotations of the output pinion gear 23 and the number of teeth of the output pinion gear 23. The output pinion gear 23 rotates by a value divided by the number of teeth of the fixed pinion gear 22, The number of teeth of the gear 33 is exceeded.

In the planetary gear train according to the first embodiment of the present invention, the number of teeth of the output ring gear and the number of teeth of the fixed ring gear that is geared on the fixed ring gear coaxially with the pinion gear So that the output ring gear is further rotated or rotated by the difference in the number of teeth through which the output pinion gear is gear-coupled with the output ring gear, thereby realizing a large gear ratio.

When the two pinion gears (the fixed pinion gear 22 and the output pinion gear 23) are the same, if the difference in the number of teeth of the two pinion gears constituting the double gear 21 is 1, The difference in the number of teeth between the stationary ring gear 32 and the output ring gear 33 becomes 1 under the condition that the centers of the gears coincide with each other.

Therefore, the gear ratio of the planetary gear train according to the first embodiment of the present invention has the following relationship.

Figure 112015082421524-pat00004

The number of teeth of the input ring gear 10 is 30, the number of teeth of the fixed ring gear 32 is 90, the number of teeth of the output ring gear 33 is 91, the number of teeth of the output pinion gear 23 is 31, 22 is 30, the gear ratio of the planetary gear train is calculated using Equation (1) as follows.

Figure 112015082421524-pat00005

When the number of teeth of the fixed ring gear 32 is 91 and the number of teeth of the output ring gear 33 is 90 by changing the roles of the fixed ring gear 32 and the output ring gear 33, The gear ratio is given by Equation (1).

Figure 112015082421524-pat00006

As described above, in the planetary gear train according to the first embodiment of the present invention, when the modules of the two pinion gears constituting the double gear 21 are the same, the difference in the number of teeth of the two pinion gears is reduced, If the difference in the number of teeth between the two ring gears is the same as the difference in the number of teeth of the pinion gear, the centers of the two pinion gears coincide.

Therefore, when one pinion gear of the two pinion gears revolves around one of the two ring gears, the difference in the number of teeth of the two pinion gears through the two ring gears A large difference in gear ratio can be realized.

In the planetary gear train according to the first embodiment of the present invention, when two modules of the pinion gears constituting the double gear 21 are different, the number of teeth n1 of the fixed pinion gear 22, The number of teeth n2 of the gear 23 and the number N1 of teeth of the fixed ring gear 32 and the number N2 of teeth of the output ring gear 33 satisfy the relationship of the following expression (4) or .

In the planetary gear train according to the first embodiment of the present invention, when the fixed pinion gear 22 revolves around the fixed ring gear 32, an output pinion gear 23 that rotates as the fixed pinion gear 22 Satisfies the following formula (2) when the number of teeth of the output ring gear (33) is smaller than the number of teeth of the output ring gear (33).

Figure 112015082421524-pat00007

The number of teeth of the output pinion gear 23 which rotates together with the fixed pinion gear 22 through the output ring gear 33 when the fixed pinion gear 22 rotates around the fixed ring gear 32, When the number of teeth is two or more than the number of teeth of the gear 33, the following equation (3) is satisfied.

Figure 112015082421524-pat00008

The left sides of the equations (2) and (3) are the gear centers of the fixed pinion gears 22 and the right sides of the equations (2) and (3) are the gear centers of the output pinion gears 23. Here, the gear center means the distance between the axes of the ring gear and the pinion gear.

Therefore, the gear ratio of the planetary gear train composed of the two pinion gears and the two ring gears satisfying the expression (2) can be calculated by applying Equation (1)

Figure 112015082421524-pat00009

Here, s is the number of teeth of the input line gear.

The gear ratio of the planetary gear train composed of the two pinion gears and the two ring gears satisfying Equation (5) is calculated by applying Equation (1) and has the following equation.

Figure 112015082421524-pat00010

Here, s is the number of teeth of the input line gear.

If the module m1 of the fixed pinion gear 22 is 0.4, the module m2 of the output pinion gear 23 is 0.5, the number n1 of teeth of the fixed pinion gear 22 is 45, The number N2 of teeth of the output ring gear is 107 and the number N2 of teeth of the output ring gear is 107 when the number of teeth n2 of the fixed ring gear 32 is 135 and the number of teeth N1 of the fixed- When the number of teeth of the planetary gear train is 45, the gear ratio of the planetary gear train can be calculated by Equation (5) as follows.

Figure 112015082421524-pat00011

The number of teeth of the fixed pinion gear 22 is n2, the number of teeth of the output pinion gear 23 is n1, and the number of teeth of the fixed ring gear And the number of teeth of the output ring gear is N1, the gear ratio of the planetary gear train can be calculated by applying Equation (1) to the following Equation (6) and Equation (7).

Figure 112015082421524-pat00012

Figure 112015082421524-pat00013

If the number of teeth of the fixed ring gear 32 is 107 and the number of teeth of the output ring gear 33 is 135 by changing the roles of the fixed ring gear 32 and the output ring gear 33, The gear ratio of the planetary gear train is calculated as follows.

Figure 112015082421524-pat00014

In the planetary gear train according to the first embodiment of the present invention, when the number of teeth of two pinion gears and the number of teeth of two ring gears satisfy Equation 2 or Equation 3, the number of teeth of the fixed pinion gear 22 The fixed pinion gear 22 and the fixed ring gear 32 each having one or more than one tooth of the fixed ring gear 32 do not change the gear centers of the fixed pinion gears so that the fixed pinion gears 22, A planetary gear train having a large gear ratio can be realized by the stationary ring gear 22 and the stationary ring gear 32.

Similarly, when the number of teeth of the two pinion gears and the number of teeth of the two ring gears satisfy Equation 2 or Equation 3, the number of teeth of the output pinion gear 23 is greater than the number of teeth of the output ring gear 33, The output pinion gear 23 and the output ring gear 33 do not change the gear centers of the output pinion gears so that the output pinion gear 23 and the output ring gear 33 each having one or more teeth each have a gear ratio of A large planetary gear train can be realized.

The number of teeth n1 of the fixed pinion gear 22 is 45, the number of teeth n2 of the output pinion gear 23 is 35, the number N1 of teeth of the fixed ring gear 32 is 135, When the number of teeth (N2) of the gear is 107, the gear ratio is as follows.

Figure 112015082421524-pat00015

However, when the number of teeth of the fixed pinion gear is 44 and the number of teeth of the fixed ring gear is 134, the gear center is equal to 18, the number of teeth of the fixed pinion gear is 45 and the number of teeth of the fixed ring gear is 135, Respectively.

Figure 112015082421524-pat00016

That is, the gear ratio becomes very large.

It is preferable that three or four double gears 21 of the planetary gear train according to the first embodiment of the present invention are provided. If the number of the double gears 21 is three, the number of teeth of the input sun gear 10 should be a multiple of three. Also, the number of teeth of the ring gear that is to be engaged with the pinion gear that is gear-coupled with the input line gear 10 must be a multiple of three. If there are four double gears 21, the number of teeth of the input sun gear 10 should be an even number. Also, the number of teeth of the ring gear that is gear-coupled with the pinion gear that is gear-coupled to the input sun gear 10 must be an even number.

In the case where the above conditions are not satisfied when three or four double gears such as the planetary gear train according to the first embodiment of the present invention are provided, the planetary gear train according to the second embodiment of the present invention Will be described in detail.

7 is a perspective view showing a planetary gear train according to a second embodiment of the present invention. 8 is a perspective view showing a triple gear 149 of the planetary gear train according to the second embodiment of the present invention. 7 to 8, the planetary gear train according to the second embodiment of the present invention includes a planetary carrier including a plurality of triple gears 149 consisting of three pinion gears, one of the three pinion gears An output ring gear (33) gear-coupled to the outside of another pinion gear of the three pinion gears and outputting a rotational force, and a pinion gear And an input sun gear 111 that meshes with the other one of the pinion gears and receives rotational force.

In the planetary gear train according to the second embodiment of the present invention, the triple gear 149 is composed of an input pinion gear 141, a fixed pinion gear 142, and an output pinion gear 143.

The input pinion gear 141 is gear-engaged with the input pinion gear 111 and the fixed pinion gear 142 is gear-engaged with the fixed ring gear 132. The output pinion gear 143 is connected to the output And gears with the ring gear 133.

The planetary gear train according to the second embodiment of the present invention is configured such that when the stationary pinion gear 142 gearing with the stationary ring gear 132 rotates around the stationary ring gear 132, And the number of teeth of the output pinion gear 143 provided on the same axis as the fixed pinion gear 142 and gear-coupled with the output ring gear 133, Or less, while achieving a large gear ratio.

Therefore, the gear ratio of the planetary gear train according to the second embodiment of the present invention has the following relationship.

Figure 112015082421524-pat00017

In the planetary gear train according to the second embodiment of the present invention, when the modules of the fixed pinion gear 142 and the output pinion gear 143 constituting the triple gear 149 are different, the fixed pinion gear 142, The number of teeth n1 of the output ring gear 133 and the number of teeth n2 of the output ring gear 132 are the same as the numbers It is preferable to have the relationship of the expression (9) or (10).

Figure 112015082421524-pat00018

Here, m1 is a module of the fixed pinion gear 142, and m2 is a module of the output pinion gear 143. [

Figure 112015082421524-pat00019

The left side of Equation (9) is the gear center of the fixed pinion gear (142), and the right side of Equation (10) is the gear center of the output pinion gear (143).

The gear ratio of the planetary gear train composed of two pinion gears having more or fewer teeth than the teeth of the two pinion gears and two ring gears having more or fewer teeth than the number of teeth of the two ring gears, The gear ratio is calculated using the following equation.

Figure 112015082421524-pat00020

Figure 112015082421524-pat00021

Here, s is the number of teeth of the input line gear and r is the number of teeth of the input pinion gear.

In the case of the planetary gear train satisfying the expressions (9) and (10), since the fixed ring gear 132 and the output ring gear 133 have no difference in the number of revolutions, (132). However, in the case of the planetary gear train satisfying the equations (11) and (12), since the gear center of the pinion gear does not change, a very small rotation speed difference is generated between the two ring gears.

The module m1 of the fixed pinion gear 142 is 0.4, the module m2 of the output pinion gear 143 is 0.5, the number n1 of teeth of the fixed pinion gear 142 is 30, The number of teeth N2 of the output pinion gear 143 is 24 and the number N2 of teeth of the output ring gear 133 is 60. The two pinion gears and two ring gears (9) and (10) are satisfied.

Two pinion gears, one of which is smaller than the number of teeth of the two pinion gears, and two ring gears, which are smaller than the number of teeth of the two ring gears, are the same as the original gear center 18 of the two pinion gears. Therefore, the gear ratio of the planetary gear train can be calculated by Equation (13) as follows.

Figure 112015082421524-pat00022

When the input pinion gear module is 0.4, the number of teeth (s) of the input sun gear and the number of teeth (r) of the input pinion gear are set to be equal to each other when the gear center of the two pinion gears coincides with the gear center of the input pinion gear. Respectively.

It should be noted that although the planetary gear train of Equation (11) or (12) has a large gear ratio, it is rare that the number of teeth of the input line gear becomes an even number or a multiple of 3 together with the stationary ring gear or the output ring gear. It is difficult to configure the planetary gear train according to the first embodiment of Fig.

Hereinafter, a planetary gear train according to a third embodiment of the present invention will be described in detail with reference to the accompanying drawings.

9 is a perspective view showing a planetary gear train according to a third embodiment of the present invention. 8 is a perspective view showing a triple gear 149 of the planetary gear train according to the third embodiment of the present invention. 10 is an exploded perspective view showing a coupling relationship between the triple gear 149 and the sun gear according to the second embodiment of the present invention. 11 is an exploded perspective view showing a coupling relationship between the triple gear 149 and the sun gear according to the third embodiment of the present invention.

8 to 11, the planetary gear train according to the third embodiment of the present invention includes a planetary carrier including a plurality of triple gears 149, each of which is composed of three pinion gears, one of the three pinion gears An output sun gear 113 that meshes with the inside of another pinion gear of the three pinion gears and outputs a rotational force, and a pinion gear And an input sun gear 111 that meshes with the other one of the pinion gears and receives rotational force.

In the planetary gear train according to the third embodiment of the present invention, the triple gear 149 is composed of an input pinion gear 141, a fixed pinion gear 142, and an output pinion gear 143.

The input pinion gear 141 is gear-coupled to the input pinion gear 111. The fixed pinion gear 142 is gear-engaged with the fixed pinion gear 112. The output pinion gear 143 is connected to the output And gears with the sun gear 113.

The planetary gear train according to the third embodiment of the present invention is configured such that when the stationary pinion gear 142 to be engaged with the stationary sun gear 112 circulates around the stationary sun gear 112, And the number of teeth of the output pinion gear 143 provided on the same axis as the fixed pinion gear 142 and gear-coupled with the output pinion gear 113 is greater than the number of teeth of the output pinion gear 142, Or less, while achieving a large gear ratio.

Therefore, the gear ratio of the planetary gear train according to the third embodiment of the present invention has a relationship as expressed by the following equation.

Figure 112015082421524-pat00023

In the planetary gear train according to the third embodiment of the present invention, the number of teeth n1 of the fixed pinion gear 142, the number n2 of teeth of the output pinion gear 143, The number of teeth N1 and the number of teeth N2 of the output sun gear 113 satisfy the following equations (14) and (15).

Figure 112015082421524-pat00024

Figure 112015082421524-pat00025

Here, m1 is a module of the fixed pinion gear 142, and m2 is a module of the output pinion gear 143. [

The left side of Equation 14 is the gear center of the fixed pinion gear 142 and the right side of Equation 14 is the gear center of the output pinion gear 143. [

The gear ratio of the planetary gear train composed of two pinion gears which are one or more than the number of teeth of the two pinion gears and two sun gears which are smaller than or greater than the number of teeth of the two sun gears, The following equation is obtained.

Figure 112015082421524-pat00026

Figure 112015082421524-pat00027

Here, s is the number of teeth of the input line gear and r is the number of teeth of the input pinion gear.

The output line gear 113 and the output line gear 113 of the planetary gear train that satisfy the equations (14) and (15) It is stopped with. However, the number of teeth of the pinion gears satisfies the equations (16) and (17) is two or less than the number of teeth of the two pinion gears, and the number of the sun gears of the two planetary gear trains There is a very small difference in the number of revolutions between the two sun gears, so that a large gear ratio can be realized.

The module m1 of the fixed pinion gear 142 is 0.4, the module m2 of the output pinion gear 143 is 0.5, the number of teeth n1 of the fixed pinion gear 142 is 30, The number of teeth N2 of the output pinion gear 143 is 24 and the number N2 of teeth of the output sun gear 133 is 48. The two pinion gears and two sun gears Equations (14) and (15) are satisfied.

However, the two pinion gears and the two sun gears, which are one in number smaller than the number of teeth of the two pinion gears and one in number greater than the number of teeth of the two sun gears, The gear ratio of the gear train has the following relationship from Equation (17).

Figure 112015082421524-pat00028

When the input pinion gear module is 0.4, the number of teeth (s) of the input sun gear and the number of teeth (r) of the input pinion gear are set to be equal to each other when the gear center of the two pinion gears coincides with the gear center of the input pinion gear. Respectively.

In the planetary gear train according to the third embodiment of the present invention, when the fixed pinion gear 142 rotates around the fixed pinion gear 112, the output pinion gear 143 Is equal to or smaller than the number of teeth of the output line gear 113 is equal to or smaller than the number of teeth of the output line gear 113, the following expression (18) is satisfied.

Figure 112015082421524-pat00029

When the fixed pinion gear 142 rotates around the fixed pinion gear 112, the number of teeth of the output pinion gear 143, which rotates together with the fixed pinion gear 142, When the number of teeth of the gear 113 is smaller or larger than the number of teeth of the gear 113, the following equation (19) is satisfied.

Figure 112015082421524-pat00030

Here, the left sides of the equations (18) and (19) are the gear centers of the fixed pinion gears 142 and the right sides of the equations (18) and (19) are the gear centers of the output pinion gears 143.

Therefore, the gear ratio of the planetary gear train composed of the two pinion gears and the two ring gears satisfying the expression (18) can be calculated by applying Equation (3) to the following equation.

Figure 112015082421524-pat00031

The gear ratio of the planetary gear train composed of the two pinion gears and the two ring gears satisfying the expression (19) is calculated by applying Equation (3) and has the following equation.

Figure 112015082421524-pat00032

If the module m1 of the fixed pinion gear 142 is 0.4, the module m2 of the output pinion gear 143 is 0.3, the number n1 of teeth of the fixed pinion gear 142 is 40, The number of teeth n2 of the output sun gear is 107 and the number of teeth of the output pinion gear N1 of the fixed pinion gear is 112. When the number of teeth n2 of the pinion gears 143 and 143 is 53 and the number of teeth N1 of the fixed stationary line gear 112 is 80, The number of teeth s of the input line gear and the number of teeth r of the input pinion gear are 80 when the input pinion gear module is 0.3 under the condition of matching the gear center of the gear with the gear center of the input pinion gear, The gear ratio of the train is calculated by the following equation (20).

Figure 112015082421524-pat00033

The number of teeth of the fixed pinion gear 142 is n2 and the number of teeth of the output pinion gear 143 is n1 and the number of teeth of the fixed pinion gear 142 is n1, And the number of teeth of the output sun gear is N1, the gear ratio of the planetary gear train is calculated by applying Equation (3) to Equation (22) and Equation (23).

Figure 112015082421524-pat00034

Figure 112015082421524-pat00035

If the number of teeth of the fixed line gear 112 is 107 and the number of teeth of the output line gear 113 is 80 by changing the roles of the fixed line gear 112 and the output line gear 113, The gear ratio of the planetary gear train is calculated as follows.

Figure 112015082421524-pat00036

In the planetary gear train according to the third embodiment of the present invention, when the number of teeth of the two pinion gears and the number of teeth of the two ring gears satisfy Equation (18) or (19), the number of teeth of the fixed pinion gear The fixed pinion gear 142 and the fixed pinion gear 112, which are one or more smaller than the number of teeth of the fixed pinion gear 112 and have a smaller or larger number of teeth than the fixed pinion gear 112, Or the small fixed pinion gear 142 and the fixed pinion gear 112 can realize a planetary gear train having a large gear ratio.

Similarly, when the number of teeth of the two pinion gears and the number of teeth of two ring gears satisfy Equation (18) or (19), the number of teeth of the output pinion gear (143) Since the output pinion gear 143 and the output pinion gear 143 have a smaller or larger number of teeth than the number of teeth of the output pinion gear 143, 113), a planetary gear train having a large gear ratio can be implemented.

If the module m1 of the fixed pinion gear 142 is 0.4, the module m2 of the output pinion gear 143 is 0.3, the number n1 of teeth of the fixed pinion gear 142 is 38, And the number of teeth N2 of the output sun gear is 102 when the number of teeth n2 of the pinion gears 143 and 143 is 50 and the number of teeth N1 of the fixed stationary gear 112 is 76, When the input pinion gear module is 0.3 and the number of teeth of the input line gear s and the number of teeth r of the input pinion gear are 76 under the condition of matching the gear center of the gear with the gear center of the input pinion gear, The gear ratio of the train is calculated by the following equation (21).

Figure 112015082421524-pat00037

However, when the number of teeth of the output pinion gear is 51 and the number of teeth of the output line gear is 101, the center of the gear is the same as the gear center having the number of teeth of the output pinion gear of 50 and the number of teeth of the output line gear of 102, The calculation is as follows.

Figure 112015082421524-pat00038

That is, the gear ratio is doubled.

Hereinafter, a method of assembling a planetary gear train according to a first embodiment of the present invention will be described in detail with reference to the accompanying drawings.

The planetary gear train according to the first embodiment of the present invention is positioned on the angular position of the pinion gear according to the position of the double gear 21 or the triple gear 149. [ Therefore, the ring gear and the sun gear to be engaged with the pinion gear must be assembled in this order.

The position of the sun gear or the ring gear assembled with the double gear 21 or the triple gear 149 must be maintained at the initial position so that the position of the assembled double gear 21 or the triple gear 149 is not changed. In addition, it is preferable to assemble the pinion gear to the shaft in a forced fit manner so that the position of the angle of the pinion gear constituting the double gear 21 or the triple gear 149 is not changed.

First, the assembling process of the planetary gear train according to the first embodiment of the present invention will be described in detail with reference to the accompanying drawings.

12 to 14 are views showing a process of assembling the planetary gear train according to the first embodiment of the present invention.

Referring to Figs. 12 to 14, the fixed pinion gear 42 is press-fitted into the gear shaft 24 knurled on the outer side. The gear shaft 24 to which the fixed pinion gear 42 is assembled is assembled to the carrier plate 25 and the fixed pinion gear 42 is engaged with the fixed ring gear 32 by gearing. The output ring gear 33 is assembled to the fixed ring gear 32 and the output pinion gear 43 is fitted to the output ring gear 33 and pressed into the gear shaft 24 to be assembled. The carrier plate 25 and the stationary ring gear 32 are maintained in an assembled state so that the position of the double gear 21 is not changed.

Next, an assembling process of the planetary gear train according to the third embodiment of the present invention will be described in detail with reference to the accompanying drawings.

15 to 18 are views showing a process of assembling the planetary gear train according to the third embodiment of the present invention.

15 to 18, the input pinion gear 141 is press-fitted into the gear shaft 144 which is knurled on the outer surface. The gear shaft 144 with the input pinion gear 141 is coupled to the carrier plate 145 and the input pinion gear 141 is fitted to the input pinion gear 111. The fixed pinion gear 142 is fixed to the fixed pinion gear 112 and the pinion gear 142 is pressed into the gear shaft 144 and assembled. The output gear gear 113 is fitted to the gear shaft 144 and assembled with the fixed gear gear 112 so that the position of the triple gear 149 is not changed, (112) is maintained.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is to be understood that the invention is not limited to the disclosed exemplary embodiments, but, on the contrary, And it goes without saying that the invention belongs to the scope of the invention.

10: input line gear
20: Planetary carrier
21: Double gear
22: Fixed pinion gear
23: Output pinion gear
24; Gear shaft
25: carrier plate
30: ring gear
32: Fixed ring gear
33: Output ring gear
111: input line gear
112: fixed line gear
113: Output line gear
141: Input pinion gear
142: Fixed pinion gear
143: Output pinion gear
144; Gear shaft
145: carrier plate
149: Triple gear

Claims (8)

delete delete delete delete A planetary carrier including a plurality of triple gears including a fixed pinion gear, an output pinion gear, and an input pinion gear;
A stationary ring gear that is gear-engaged outside the stationary pinion gear;
An output ring gear that is gear-engaged outside the output pinion gear; And
An input line gear that meshes inside the input pinion gear;
And a planetary gear train. The planetary gear train according to claim 5, wherein the gear ratio of the planetary gear train
Figure 112015082421524-pat00040

Of the planetary gear train. A planetary carrier including a plurality of triple gears including a fixed pinion gear, an output pinion gear, and an input pinion gear;
A fixed line gear that is gear-engaged inside the fixed pinion gear;
An output line gear that meshes with the inside of the output pinion gear; And
An input line gear that meshes inside the input pinion gear;
And a planetary gear train. The planetary gear train according to claim 7, wherein the gear ratio of the planetary gear train
Figure 112015082421524-pat00041
Of the planetary gear train.
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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000346149A (en) * 1999-06-01 2000-12-12 Minoru Nakagawa Sun gear self-operated reversing drive type self- operated differential generator
JP3533735B2 (en) * 1994-12-16 2004-05-31 富士写真フイルム株式会社 Planetary gear mechanism
JP2009052743A (en) 2007-08-27 2009-03-12 Ford Global Technologies Llc Planetary gear train

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3533735B2 (en) * 1994-12-16 2004-05-31 富士写真フイルム株式会社 Planetary gear mechanism
JP2000346149A (en) * 1999-06-01 2000-12-12 Minoru Nakagawa Sun gear self-operated reversing drive type self- operated differential generator
JP2009052743A (en) 2007-08-27 2009-03-12 Ford Global Technologies Llc Planetary gear train

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