Planetary gear reducer

Abstract

The planetary gear reducer according to an embodiment of the present invention comprises: a first ring gear engaging with the lower parts of a plurality of planetary gears; and a second ring gear engaging with the upper parts of the plurality of planetary gears and having a greater number of teeth than the first ring gear, thereby outputting an increased reduction gear ratio compared to the prior art.

Description

planetary gear reducer

[0001] The present invention relates to a planetary gear reducer, and more particularly, to a planetary gear reducer capable of outputting a reduction ratio increased compared to a conventional gear reducer through a plurality of planetary gears and two ring gears meshed with the plurality of planetary gears.

[0002] Typically, a planetary gear reducer is composed of a sun gear, a ring gear, planetary gears, and a carrier. The sun gear is provided at the center of the planetary gear reducer, and the ring gear is provided on the outside of the sun gear to surround the sun gear. A plurality of planetary gears are provided at equal intervals in the circumferential direction between the sun gear and the ring gear, and the carrier supports the planetary gears at equal intervals.

[0003] For example, if a sun gear is installed on an axle shaft, a ring gear on a housing, and a carrier on the wheel hub, and the ring gear is fixed and then driven, the carrier is decelerated. Therefore, when the sun gear is rotated by power transmitted from the engine, the planetary gear rotates along the inner surface of the ring gear, and the carrier drives the wheel, thereby decelerating the wheel and generating a large driving force.

[0004] In general, in a planetary gear reducer, the number of teeth of the sun gear and the number of teeth of the ring gear are added together and divided by the number of planetary gears to obtain an integer. For example, if the number of planetary gears is 3, [(number of teeth of sun gear) + (number of teeth of ring gear) / 3] = integer. In this case, the planetary gears are arranged one at a time so that they have a central angle of 120 degrees in the circumferential direction.

[0005] However, conventional planetary gear reducers have the problem of difficulty in producing high reduction ratios when the number of ring gear teeth is large. Furthermore, conventional reducers have complex structures and numerous components, making installation and maintenance difficult.

[0006] In addition, an object of the present invention is to provide a planetary gear reducer capable of outputting a reduction ratio increased compared to the conventional one through a first planetary gear formed of a first lower gear and a first upper gear having the same phase difference as the first lower gear, a second planetary gear formed of a second lower gear and a second upper gear having a clockwise phase difference from the second lower gear, and a third planetary gear formed of a third lower gear and a third upper gear having a counterclockwise phase difference from the third lower gear.

[0007] In addition, an object of the present invention is to provide a planetary gear reducer capable of outputting a reduction ratio increased compared to the conventional one through a first ring gear that meshes with the lower portions of a plurality of planetary gears and a second ring gear that meshes with the upper portions of the plurality of planetary gears and has a larger number of teeth than the first ring gear.

[0008] In addition, an object of the present invention is to provide a planetary gear reducer that is simple in structure and has a small number of components, making it easy to install and maintain.

[0009] According to one embodiment of the present invention, a planetary gear reducer includes a first drive motor (6) that rotates by electric power, a carrier (10) that is axially coupled to the first drive motor (6) and rotates by the power of the first drive motor (6), a first outer gear (20) that is rotatably coupled to the carrier (10) and rotates by the carrier (10), a first ring gear (31) that engages with the lower portion of the first outer gear (20) and outputs a rotation speed reduced from the rotation speed of the carrier (10) by being rotated by the first outer gear (20), and a second ring gear (32) that engages with the upper portion of the first outer gear (20) and outputs a rotation speed reduced from the rotation speed of the carrier (10) by being rotated by the first outer gear (20), and a lower portion of the carrier (10) is provided with a first drive motor (6) and a second ring gear (32) that outputs a rotation speed reduced from the rotation speed of the carrier (10). A power-transmitting disk portion (11) is formed, and a first coupling pin (12) is formed to protrude upwardly on the upper rear surface of the disk portion (11), a second coupling pin (13) is formed to protrude upwardly on the front left side of the upper surface of the disk portion (11), and a third coupling pin (14) is formed to protrude upwardly on the front right side of the upper surface of the disk portion (11), and the first outer gear (20) is rotatably coupled to the first coupling pin (12), and a first planetary gear (21) that engages with the first ring gear (31) and the second ring gear (32), respectively, a second planetary gear (22) that is rotatably coupled to the second coupling pin (13) and engages with the first ring gear (31) and the second ring gear (32), respectively, and is rotatably coupled to the third coupling pin (14), and the first ring gear (31) and It is characterized by including a third planetary gear (23) that meshes with the second ring gear (32).

[0010] In addition, a first lower gear (21-1) is formed on the outer circumference with a first preset number of teeth formed in the circumferential direction so as to be engaged with the first ring gear (31) at the lower portion of the first planetary gear (21), and a first upper gear (21-2) is formed integrally with the first lower gear (21-1) on the upper portion of the first planetary gear (21), and a second lower gear (22-1) is formed on the outer circumference with a first preset number of teeth formed in the circumferential direction so as to be engaged with the second ring gear (32), and a second lower gear (22-1) is formed on the lower portion of the second planetary gear (22), and a second lower gear (22-1) is formed on the outer circumference with a first preset number of teeth formed in the circumferential direction so as to be engaged with the first ring gear (31), and a second upper gear (22) is formed on the outer circumference with a first preset number of teeth formed in the circumferential direction so as to be engaged with the second ring gear (32) at the upper portion of the second planetary gear (22). A second upper gear (22-2) formed in a circumferential direction as many as the number of settings is formed integrally with the second lower gear (22-1), and the second upper gear (22-2) is formed in a shape in which the second lower gear (22-1) is rotated clockwise by a first reference angle set in advance based on the central axis of the second lower gear (22-1), and the first reference angle is set to a value obtained by dividing 120° by the first number of settings.

[0011] In addition, a third lower gear (23-1) is formed on the outer surface of the third planetary gear (23) so that it can mesh with the first ring gear (31) and has teeth formed in the circumferential direction as many as the first setting number, and a third upper gear (23-2) is formed integrally with the third lower gear (23-1) so that it can mesh with the second ring gear (32) and has teeth formed in the circumferential direction as many as the first setting number, on the outer surface of the third planetary gear (23), and the third upper gear (23-2) is characterized in that it is formed in a shape in which the third lower gear (23-1) is rotated counterclockwise by a first reference angle based on the central axis of the third lower gear (23-1).

[0012] In addition, the inner surface of the first ring gear (31) is formed with teeth in the circumferential direction as many as a first reference number set in advance, and the inner surface of the second ring gear (32) is formed with teeth in the circumferential direction as many as a second reference number set in advance, and the second reference number is set to a value obtained by adding 1 to the first reference number.

[0013] In addition, it further includes a second driving motor (40) that rotates by electric power and a sun gear (45) that is axially coupled to the second driving motor (40) and rotates by the power of the second driving motor, and the sun gear (45) is provided between the first lower gear (21-1), the second lower gear (22-1) and the third lower gear (23-1), and is meshed with the first lower gear (21-1), the second lower gear (22-1) and the third lower gear (23-1), respectively, to transmit the power of the second driving motor (40) to the first lower gear (21-1), the second lower gear (22-1) and the third lower gear (23-1), and is characterized in that teeth are formed in the circumferential direction on the outer surface of the sun gear (45) in a standard number set in advance.

[0014] A planetary gear reducer according to one embodiment of the present invention has the effect of being able to output a reduction ratio that is increased compared to the conventional one through a first planetary gear formed of a first lower gear and a first upper gear having the same phase difference as the first lower gear, a second planetary gear formed of a second lower gear and a second upper gear having a clockwise phase difference from the second lower gear, and a third planetary gear formed of a third lower gear and a third upper gear having a counterclockwise phase difference from the third lower gear.

[0015] A planetary gear reducer according to one embodiment of the present invention has the effect of being able to output a reduction ratio that is increased compared to the conventional one through a first ring gear that meshes with the lower portions of a plurality of planetary gears and a second ring gear that meshes with the upper portions of the plurality of planetary gears and has a larger number of teeth than the first ring gear.

[0016] A planetary gear reducer according to an embodiment of the present invention has a simple structure and does not have many components, so it is easy to install and maintain.

[0017] FIG. 1 is a perspective view of a planetary gear reducer according to an embodiment of the present invention.

[0018] Figure 2 is an exploded view of the planetary gear reducer shown in Figure 1.

[0019] Figure 3 is a plan view of the planetary gear reducer illustrated in Figure 1.

[0020] Figure 4 is a detailed drawing of the first planetary gear, the second planetary gear, and the third planetary gear.

[0021] Figure 5 is a plan view for explaining the relationship between the first planetary gear, the second planetary gear, the third planetary gear, the first ring gear, and the second ring gear.

[0022] Fig. 6 is a plan view of a planetary gear reducer equipped with a sun gear.

[0023] Fig. 7 is a plan view of a planetary gear reducer according to a second embodiment of the present invention.

[0024] Figure 8 is a plan view of a planetary gear reducer according to a third embodiment of the present invention.

[0025] Figure 9 is a table regarding the angular velocities of the sun gear, the second upper gear, the second lower gear, the first ring gear, and the second ring gear.

[0026] Hereinafter, in order to explain in detail to a degree that a person having ordinary skill in the art to which the present invention pertains can easily practice the technical idea of ​​the present invention, an embodiment of the present invention will be described with reference to the attached drawings.

[0027] However, the following examples are merely examples intended to aid understanding of the present invention and are not intended to limit or reduce the scope of the present invention. Furthermore, the present invention may be embodied in various different forms and is not limited to the examples described herein.

[0028] FIG. 1 is a perspective view of a planetary gear reducer (5) according to an embodiment of the present invention, FIG. 2 is an exploded view of the planetary gear reducer (5) illustrated in FIG. 1, and FIG. 3 is a plan view of the planetary gear reducer (5) illustrated in FIG. 1.

[0029] Referring to FIGS. 1 to 3, a planetary gear reducer (5) according to one embodiment of the present invention is configured to include a first drive motor (6) (not shown), a carrier (10), a first outer gear (20), a first ring gear (31), and a second ring gear (32).

[0030] First, the first drive motor (6) rotates by electric power.

[0031] And, the carrier (10) is axially coupled to the first driving motor (6) and rotates by the power of the first driving motor (6).

[0032] Specifically, the carrier (10) transmits the power of the first drive motor (6) to the first outer gear (20).

[0033] And, the first outer gear (20) is rotatably connected to the carrier (10) and rotates by the carrier (10).

[0034] And, the first ring gear (31) is engaged with the lower portion of the first outer gear (20) and rotates by the first outer gear (20), thereby outputting a rotation speed that is reduced from the rotation speed of the carrier (10).

[0035] And, the second ring gear (32) is engaged with the upper portion of the first outer gear (20) and rotates by the first outer gear (20), thereby outputting a rotation speed that is reduced from the rotation speed of the carrier (10).

[0036] Meanwhile, a disc portion (11) is formed at the bottom of the carrier (10) to which power is transmitted from the first driving motor (6).

[0037] And, a first coupling pin (12) is formed to protrude upward on the upper rear surface of the above-mentioned disc portion (11).

[0038] And, a second coupling pin (13) is formed to protrude upward on the front left side of the upper surface of the above-mentioned disc portion (11).

[0039] And, a third coupling pin (14) is formed to protrude upward on the front right side of the upper surface of the above-mentioned disc portion (11).

[0040] Meanwhile, the first outer gear (20) is configured to include a first planetary gear (21), a second planetary gear (22), and a third planetary gear (23).

[0041] First, the first planetary gear (21) is rotatably connected to the first coupling pin (12) and meshes with the first ring gear (31) and the second ring gear (32), respectively.

[0042] And, the second planetary gear (22) is rotatably connected to the second coupling pin (13) and meshes with the first ring gear (31) and the second ring gear (32), respectively.

[0043] And, the third planetary gear (23) is rotatably connected to the third coupling pin (14) and meshes with the first ring gear (31) and the second ring gear (32), respectively.

[0044] Meanwhile, a first through hole (21a) is formed through the center of the upper surface of the first planetary gear (21) so that it can be rotatably coupled to the first coupling pin (12).

[0045] And, a second through hole (22a) is formed through the center of the upper surface of the second planetary gear (22) so that it can be rotatably coupled to the second coupling pin (13).

[0046] And, a third through hole (23a) is formed through the center of the upper surface of the third planetary gear (23) so that it can be rotatably coupled to the third coupling pin (14).

[0047] Fig. 4 is a detailed drawing of the first planetary gear (21), the second planetary gear (22), and the third planetary gear (23). Referring to Fig. 4, a first lower gear (21-1) is formed on the lower portion of the first planetary gear (21) so that teeth are formed in the circumferential direction on the outer surface as a first setting number set in advance so as to be meshed with the first ring gear (31). At this time, the first setting number can be set to 18.

[0048] And, on the upper part of the first planetary gear (21), a first upper gear (21-2) having teeth formed in the circumferential direction as many as the first set number on the outer surface so as to be meshed with the second ring gear (32) is formed integrally with the first lower gear (21-1).

[0049] And, at the lower portion of the second planetary gear (22), a second lower gear (22-1) is formed with teeth formed in the circumferential direction on the outer surface as many as the first setting number so as to be meshed with the first ring gear (31).

[0050] And, on the upper part of the second planetary gear (22), a second upper gear (22-2) having teeth formed in the circumferential direction as many as the first setting number on the outer surface so as to be meshed with the second ring gear (32) is formed integrally with the second lower gear (22-1).

[0051] At this time, the second upper gear (22-2) is formed in a shape in which the second lower gear (22-1) is rotated clockwise by a first reference angle set in advance based on the central axis of the second lower gear (22-1).

[0052] Here, the first reference angle is set to a value obtained by dividing 120° by the first setting number. For example, if the first setting number is 18, the first reference angle can be set to 120° / 18=6.67°.

[0053] And, at the lower part of the third planetary gear (23), a third lower gear (23-1) is formed with teeth formed in the circumferential direction on the outer surface as many as the first setting number so as to be meshed with the first ring gear (31).

[0054] And, on the upper part of the third planetary gear (23), a third upper gear (23-2) having teeth formed in the circumferential direction as many as the first setting number on the outer surface so as to be meshed with the second ring gear (32) is formed integrally with the third lower gear (23-1).

[0055] At this time, the third upper gear (23-2) is formed in a shape in which the third lower gear (23-1) is rotated counterclockwise by a first reference angle based on the central axis of the third lower gear (23-1).

[0056] Meanwhile, on the inner surface of the first ring gear (31), teeth are formed in the circumferential direction as many as the first reference number set in advance. And, on the inner surface of the second ring gear (32), teeth are formed in the circumferential direction as many as the second reference number set in advance.

[0057] At this time, the second reference number is set to a value that adds 1 to the first reference number. Specifically, the first reference number may be set to 45, and the second reference number may be set to 46.

[0058] Fig. 5 is a plan view for explaining the relationship between the first planetary gear (21), the second planetary gear (22), the third planetary gear (23), the first ring gear (31), and the second ring gear (32). Referring to Fig. 5, the first ring gear (31) is indicated in blue, and the second ring gear (32) is indicated in red.

[0059] And, the second lower gear (22-1) is indicated in blue on the front left, and the second upper gear (22-2) is indicated in red on the upper side of the second lower gear. And, the third lower gear (23-1) is indicated in blue on the front right, and the first upper gear is indicated in red on the upper side of the third lower gear (23-1).

[0060] Here, the first planetary gear (21) is simultaneously engaged with the first ring gear (31) and the second ring gear (32). In addition, the second lower gear (22-1) is engaged with the first ring gear (31), and the second upper gear (22-2) is engaged with the second ring gear (32). In addition, the third lower gear (23-1) is engaged with the first ring gear (31), and the third upper gear (23-2) is engaged with the second ring gear (32).

[0061] Fig. 6 is a plan view of a planetary gear reducer (5) equipped with a sun gear (45). Referring to Fig. 6, a planetary gear reducer (5) according to an embodiment of the present invention may further include a second drive motor (40) (not shown) and a sun gear (45).

[0062] First, the second drive motor (40) rotates by electric power.

[0063] And, the sun gear (45) is axially coupled to the second driving motor (40) and rotates by the power of the second driving motor (40).

[0064] And, the sun gear (45) is provided between the first lower gear (21-1), the second lower gear (22-1), and the third lower gear (23-1), and is engaged with the first lower gear (21-1), the second lower gear (22-1), and the third lower gear (23-1), respectively, to transmit the power of the second driving motor (40) to the first lower gear (21-1), the second lower gear (22-1), and the third lower gear (23-1). At this time, the height of the sun gear (45) is formed to be the same as the height of the first lower gear (21-1).

[0065] And, on the outer surface of the sun gear (45), teeth are formed in the circumferential direction in a standard number set in advance. At this time, the standard number can be set to 9.

[0066] Fig. 7 is a plan view of a planetary gear reducer (5) according to a second embodiment of the present invention. Referring to Fig. 7, the planetary gear reducer (5) according to the second embodiment of the present invention may include two planetary gears.

[0067] Specifically, the planetary gear reducer (5) according to the second embodiment of the present invention may further include a second outer gear (50) provided on the inner side of the first ring gear (31) and the second ring gear (32). At this time, the second outer gear (50) includes a fourth planetary gear (54) and a fifth planetary gear (55).

[0068] First, the fourth planetary gear (54) is provided on the inner rear of the first ring gear (31) and the second ring gear (32), and is engaged with the first ring gear (31) and the second ring gear (32), respectively.

[0069] In addition, the fifth planetary gear (55) is provided opposite the fourth planetary gear (54) on the inner front of the first ring gear (31) and the second ring gear (32), and is engaged with the first ring gear (31) and the second ring gear (32), respectively.

[0070] Meanwhile, a fourth lower gear (54-1) is formed on the outer surface of the fourth planetary gear (54) so ​​that teeth are formed in the circumferential direction as many as the second setting number so that they can mesh with the first ring gear (31).

[0071] And, on the upper part of the fourth planetary gear (54), a fourth upper gear (54-2) having teeth formed in the circumferential direction as many as the second setting number on the outer surface so as to be meshed with the second ring gear (32) is formed integrally with the fourth lower gear (54-1). At this time, the second setting number can be set to 15.

[0072] And, at the lower portion of the fifth planetary gear (55), a fifth lower gear (55-1) is formed with teeth formed in the circumferential direction as many as the second setting number on the outer surface so that it can mesh with the first ring gear (31).

[0073] And, on the upper part of the fifth planetary gear (55), a fifth upper gear (55-2) having teeth formed in the circumferential direction as many as the second setting number on the outer surface so as to be meshed with the second ring gear (32) is formed integrally with the fifth lower gear (55-1).

[0074] At this time, the fifth upper gear (55-2) is formed in a shape in which the fifth lower gear (55-1) is rotated clockwise by a second reference angle set in advance based on the central axis of the fifth lower gear (55-1).

[0075] Here, the second reference angle is set to a value obtained by dividing 180° by the second setting number. For example, if the second setting number is 15, the second reference angle can be set to 180° / 15=12°.

[0076] Fig. 8 is a plan view of a planetary gear reducer (5) according to a third embodiment of the present invention. Referring to Fig. 8, the planetary gear reducer (5) according to the third embodiment of the present invention may include four planetary gears.

[0077] Specifically, the planetary gear reducer (5) according to the third embodiment of the present invention may further include a third outer gear (60) provided on the inner side of the first ring gear (31) and the second ring gear (32). At this time, the third outer gear (60) includes a sixth planetary gear (66), a seventh planetary gear (67), an eighth planetary gear (68), and a ninth planetary gear (69).

[0078] First, the sixth planetary gear (66) is provided on the inner rear of the first ring gear (31) and the second ring gear (32) and meshes with the first ring gear (31) and the second ring gear (32), respectively. At this time, the sixth planetary gear (66) is formed in the same shape and size as the fourth planetary gear (54).

[0079] In addition, the seventh planetary gear (67) is provided opposite the sixth planetary gear (66) on the inner front of the first ring gear (31) and the second ring gear (32), and is engaged with the first ring gear (31) and the second ring gear (32), respectively. At this time, the seventh planetary gear (67) is formed in the same shape and size as the fifth planetary gear (55).

[0080] In addition, the 8th planetary gear (68) is provided on the inner left side of the first ring gear (31) and the second ring gear (32), and is engaged with the first ring gear (31) and the second ring gear (32), respectively.

[0081] In addition, the ninth planetary gear (69) is provided opposite the eighth planetary gear (68) on the inner right side of the first ring gear (31) and the second ring gear (32), and is engaged with the first ring gear (31) and the second ring gear (32), respectively.

[0082] Meanwhile, an eighth lower gear (68-1) is formed on the outer surface of the eighth planetary gear (68) so that teeth are formed in the circumferential direction as many as the second setting number so that they can mesh with the first ring gear (31).

[0083] And, on the upper part of the eighth planetary gear (68), an eighth upper gear (68-2) having teeth formed in the circumferential direction as many as the second setting number on the outer surface so as to be meshed with the second ring gear (32) is formed integrally with the eighth lower gear (68-1).

[0084] At this time, the eighth upper gear (68-2) is formed in a shape in which the eighth lower gear (68-1) is rotated clockwise by a third reference angle set in advance based on the central axis of the eighth lower gear (68-1).

[0085] Here, the third reference angle is set to a value obtained by dividing 90° by the number of second settings. For example, if the number of second settings is 15, the third reference angle can be set to 90° / 15=6°.

[0086] And, at the lower portion of the ninth planetary gear (69), a ninth lower gear (69-1) is formed with teeth formed in the circumferential direction as many as the second setting number on the outer surface so that it can mesh with the first ring gear (31).

[0087] And, on the upper part of the ninth planetary gear (69), a ninth upper gear (69-2) having teeth formed in the circumferential direction as many as the second setting number on the outer surface so as to be meshed with the second ring gear (32) is formed integrally with the ninth lower gear (69-1).

[0088] At this time, the ninth upper gear (69-2) is formed in a shape in which the ninth lower gear (69-1) is rotated counterclockwise by the third reference angle based on the central axis of the ninth lower gear (69-1).

[0089] Meanwhile, the reduction principle of the planetary gear reducer (5) according to one embodiment of the present invention is as follows.

[0090] First, the number of teeth of the sun gear (45), the second lower gear (22-1), the second upper gear (22-2), the first ring gear (31), and the second ring gear (32) are defined as z1, z2, z3, z4, and z5, respectively.

[0091] And, z1, z2, z3, z4 and z5 are set to 9, 18, 18, 45 and 46, respectively.

[0092] And, the angular velocity of the sun gear (45) is defined as ω.

[0093] Figure 9 is a table regarding the angular velocities of the sun gear (45), the second lower gear (22-1), the second upper gear (22-2), the first ring gear (31), and the second ring gear (32).

[0094] First, when the carrier (10) is the input side and the first ring gear (31) is the output side, the reduction ratio R1 can be defined as (angular velocity of the carrier (10)) / (angular velocity of the first ring gear (31)).

[0095] After substituting the angular velocity of the carrier (10) and the angular velocity of the first ring gear (31) shown in Fig. 9 into R1, R1 is calculated as follows.

[0096] R1=(ω×z1 / z5) / [ω×(z1 / z5-z1 / z4)]=z4 / (z4-z5)=45 / (45-46)=-45

[0097]

[0098] *Therefore, the first ring gear (31) can output an angular velocity reduced to 1 / 45 of the angular velocity of the carrier (10).

[0099] Meanwhile, when the carrier (10) is the input side and the second ring gear (32) is the output side, the reduction ratio R2 can be defined as (angular velocity of the carrier (10)) / (angular velocity of the second ring gear (32)).

[0100] After substituting the angular velocity of the carrier (10) and the angular velocity of the second ring gear (32) shown in Fig. 9 into R2, R2 is calculated as follows.

[0101] R2=(ω×z1 / z4) / [ω×(z1 / z4-z1 / z5]=z5 / (z5-z4)=46 / (46-45)=46

[0102] Therefore, the second ring gear (32) can output an angular velocity reduced to 1 / 46 of the angular velocity of the carrier (10).

[0103] Meanwhile, when the sun gear (45) is the input side and the second ring gear (32) is the output side, the reduction ratio R3 can be defined as (angular velocity of the sun gear (45)) / (angular velocity of the second ring gear (32)).

[0104] After substituting the angular velocity of the sun gear (45) and the angular velocity of the second ring gear (32) shown in Fig. 9 into R3, R3 is calculated as follows.

[0105] R3=[ω×(z1 / z4+1)] / [ω×(z1 / z4-z1 / z5)]=[(z1+z4) / z4]×[z4×z5 / z1]

[0106] =(1+z4 / z1)×z5=(1+45 / 9)×46=276

[0107] Therefore, the second ring gear (32) can output an angular velocity reduced to 1 / 276 of the angular velocity of the sun gear (45).

[0108] A planetary gear reducer (5) according to one embodiment of the present invention has the effect of being able to output a reduction ratio that is increased compared to the conventional one through a first planetary gear (21) formed of a first lower gear (21-1) and a first upper gear (21-2) having the same phase difference as the first lower gear (21-1), a second planetary gear (22) formed of a second lower gear (22-1) and a second upper gear (22-2) having a clockwise phase difference from the second lower gear (22-1), and a third planetary gear (23) formed of a third lower gear (23-1) and a third upper gear (23-2) having a counterclockwise phase difference from the third lower gear (23-1).

[0109] A planetary gear reducer (5) according to one embodiment of the present invention has the effect of being able to output a reduction ratio that is increased compared to the conventional one through a first ring gear (31) that meshes with the lower portions of a plurality of planetary gears and a second ring gear (32) that meshes with the upper portions of the plurality of planetary gears and has a greater number of teeth than the first ring gear (31).

[0110] The planetary gear reducer (5) according to one embodiment of the present invention has a simple structure and does not have many components, so it is easy to install and maintain.

[0111] As described above, the present invention has as its main technical idea the purpose of providing a planetary gear reducer (5), and the embodiment described above with reference to the drawings is only one embodiment, and the true scope of the rights of the present invention is based on the scope of the patent claims, but also extends to various equivalent embodiments that may exist.

[0112] 5: Planetary gear reducer 6: First drive motor

[0113] 10: Carrier 11: Disc

[0114] 12: First coupling pin 13: Second coupling pin

[0115] 14: Third coupling pin 20: First outer gear

[0116] 21: First planetary gear 21a: First through hole

[0117] 21-1: 1st lower gear 21-2: 1st upper gear

[0118] 22: Second planetary gear 22a: Second through hole

[0119] 22-1: Second lower gear 22-2: Second upper gear

[0120] 23: Third planetary gear 23a: Third through hole

[0121] 23-1: Third lower gear 23-2: Third upper gear

[0122] 31: 1st ring gear 32: 2nd ring gear

[0123] 40: Second drive motor 45: Sun gear

[0124] 50: 2nd outer gear 54: 4th planetary gear

[0125] 54-1: 4th lower gear 54-2: 4th upper gear

[0126] 55: Fifth planetary gear 55-1: Fifth lower gear

[0127] 55-2: 5th upper gear 60: 3rd outer gear

[0128] 66: 6th planetary gear 67: 7th planetary gear

[0129] 67-1: 7th lower gear 67-2: 7th upper gear

[0130] 68: 8th planetary gear 68-1: 8th lower gear

[0131] 68-2: 8th upper gear 69: 9th planetary gear

[0132] 69-1: 9th lower gear 69-2: 9th upper gear

Claims

1. A first driving motor (6) that rotates by electric power; A carrier (10) that is axially coupled to the first driving motor (6) and rotates by the power of the first driving motor (6); A first outer gear (20) rotatably coupled to the carrier (10) and rotated by the carrier (10); A first ring gear (31) that is engaged with the lower portion of the first outer gear (20) and rotates by the first outer gear (20) to output a rotation speed that is reduced from the rotation speed of the carrier (10); and It includes a second ring gear (32) that is engaged with the upper portion of the first outer gear (20) and rotates by the first outer gear (20) to output a rotation speed that is reduced from the rotation speed of the carrier (10); A disc portion (11) is formed at the bottom of the carrier (10) to which power is transmitted from the first driving motor (6). On the upper rear surface of the above-mentioned disc portion (11), a first coupling pin (12) is formed to protrude upward, On the front left side of the upper surface of the above-mentioned disc portion (11), a second coupling pin (13) is formed to protrude upwards, On the front right side of the upper surface of the above-mentioned disc portion (11), a third coupling pin (14) is formed to protrude upwards, The above first outer gear (20) A first planetary gear (21) rotatably coupled to the first coupling pin (12) and meshed with the first ring gear (31) and the second ring gear (32), respectively; A second planetary gear (22) rotatably coupled to the second coupling pin (13) and meshed with the first ring gear (31) and the second ring gear (32), respectively; and A planetary gear reducer characterized by including a third planetary gear (23) rotatably coupled to the third coupling pin (14) and meshed with the first ring gear (31) and the second ring gear (32), respectively.

2. In paragraph 1, At the lower portion of the first planetary gear (21), a first lower gear (21-1) is formed with teeth formed in the circumferential direction as many as the first preset number of teeth on the outer surface so that they can mesh with the first ring gear (31). On the upper part of the first planetary gear (21), a first upper gear (21-2) having teeth formed in the circumferential direction as many as the first setting number on the outer surface so as to be meshed with the second ring gear (32) is formed integrally with the first lower gear (21-1). At the lower part of the second planetary gear (22), a second lower gear (22-1) is formed with teeth formed in the circumferential direction as many as the first setting number on the outer surface so that it can mesh with the first ring gear (31). On the upper part of the second planetary gear (22), a second upper gear (22-2) having teeth formed in the circumferential direction as many as the first setting number on the outer surface so as to be meshed with the second ring gear (32) is formed integrally with the second lower gear (22-1). The above second upper gear (22-2) is formed in a shape in which the second lower gear (22-1) is rotated clockwise by a first reference angle set in advance based on the central axis of the second lower gear (22-1). A planetary gear reducer, characterized in that the first reference angle is set to a value obtained by dividing 120° by the first setting number.

3. In paragraph 1, A third lower gear (23-1) is formed on the outer surface of the third planetary gear (23) so that teeth are formed in the circumferential direction as many as the first setting number so that they can mesh with the first ring gear (31). On the upper part of the third planetary gear (23), a third upper gear (23-2) having teeth formed in the circumferential direction as many as the first setting number on the outer surface so as to mesh with the second ring gear (32) is formed integrally with the third lower gear (23-1). A planetary gear reducer characterized in that the third upper gear (23-2) is formed in a shape in which the third lower gear (23-1) is rotated counterclockwise by a first reference angle based on the central axis of the third lower gear (23-1).

4. In paragraph 1, On the inner surface of the first ring gear (31), teeth are formed in the circumferential direction as many as the first reference number set in advance, On the inner surface of the second ring gear (32), teeth are formed in the circumferential direction as many as the second reference number set in advance, A planetary gear reducer, characterized in that the second reference number is set to a value obtained by adding 1 to the first reference number.

5. In paragraph 1, A second driving motor (40) that rotates by electric power; and It further includes a sun gear (45) that is axially coupled to the second driving motor (40) and rotates by the power of the second driving motor; The above-mentioned sun gear (45) is provided between the first lower gear (21-1), the second lower gear (22-1) and the third lower gear (23-1), and is engaged with the first lower gear (21-1), the second lower gear (22-1) and the third lower gear (23-1), respectively, to transmit the power of the second driving motor (40) to the first lower gear (21-1), the second lower gear (22-1) and the third lower gear (23-1). A planetary gear reducer characterized in that a predetermined standard number of teeth are formed in the circumferential direction on the outer surface of the above-mentioned sun gear (45).

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