CN107664185B - Transmission and drive unit - Google Patents
Transmission and drive unit Download PDFInfo
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- CN107664185B CN107664185B CN201710636873.5A CN201710636873A CN107664185B CN 107664185 B CN107664185 B CN 107664185B CN 201710636873 A CN201710636873 A CN 201710636873A CN 107664185 B CN107664185 B CN 107664185B
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- planetary
- rotating bodies
- axial direction
- sun gear
- planetary rotating
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 50
- 238000005096 rolling process Methods 0.000 claims abstract description 126
- 230000002093 peripheral effect Effects 0.000 claims description 20
- 229910000831 Steel Inorganic materials 0.000 description 5
- 239000010959 steel Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 239000000470 constituent Substances 0.000 description 3
- 230000037431 insertion Effects 0.000 description 3
- 238000003780 insertion Methods 0.000 description 3
- 238000005266 casting Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- WABPQHHGFIMREM-UHFFFAOYSA-N lead(0) Chemical compound [Pb] WABPQHHGFIMREM-UHFFFAOYSA-N 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
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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
- F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
- F16H13/06—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion
- F16H13/08—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion with balls or with rollers acting in a similar manner
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
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- Friction Gearing (AREA)
Abstract
The invention provides a transmission and a drive unit, which can efficiently transmit power in the transmission. The transmission (10) is provided with a sun gear (1), a plurality of 1 st planetary rotating bodies (2a), a plurality of 2 nd planetary rotating bodies (2b), a carrier (3a), an inner ring (4), a housing (5) and a shaft body (3 b). The 1 st planetary rotating bodies (2a) are arranged on one side of the 2 nd planetary rotating bodies (2b) in the axial direction. The plurality of planetary rotating bodies (2a, 2b) are rotatably held by the carrier (3a) so as to be capable of revolving about the central axis (C). The carrier (3a) rotates around a central axis (C) together with the revolution of the plurality of planetary rolling bodies (2a, 2 b). When the sun gear (1) is rotationally driven by the motor (50), the rotation of the sun gear (1) is transmitted to the shaft body (3b) after being decelerated by the plurality of planetary rotating bodies (2a, 2b) and the carrier (3 a).
Description
Technical Field
The invention relates to a transmission and a drive unit.
Background
Conventionally, a transmission that outputs a rotation of a motor rotating shaft after accelerating or decelerating the rotation has been known. For example, patent document 1 discloses a spindle capable of accelerating rotation of a shaft-like body and transmitting the accelerated rotation to a spindle (spindle).
In the rotating shaft of patent document 1, one end of the shaft-like body has a substantially cylindrical shape. Three through holes are formed in the one end portion of the shaft-like body so as to penetrate in the radial direction of the shaft-like body. The three through holes are formed at regular intervals in the circumferential direction of the shaft-like body.
The spindle of the rotating shaft is rotatably supported by a bearing. One end portion of the spindle of the rotating shaft is positioned inside the one end portion of the shaft-like body. Three steel balls (steel balls) are provided around one end of the spindle shaft so as to be inserted into the three through holes, respectively. A pair of ball receiving wheel bodies are provided in such a manner as to contact three steel balls from the radially outer side of the spindle of the rotary shaft.
In the rotating shaft of patent document 1, the steel balls revolve around the main shaft of the rotating shaft while rotating on their own axes by the rotation of the shaft-like body. The autorotation of the steel balls is transmitted to the spindle of the rotating shaft through friction force. Thereby, the rotation of the shaft-like body is accelerated and transmitted to the spindle shaft.
Documents of the prior art
Patent document
Patent document 1: japanese Kokoku publication Sho-51-29418
Disclosure of Invention
[ problems to be solved by the invention ]
However, as described above, the rotating shaft of patent document 1 supports the rotating shaft main shaft by the bearing. Therefore, the bearing becomes rotational resistance, and the power transmission efficiency from the shaft-like body to the spindle shaft is lowered.
On the other hand, if the bearing is removed from the rotating shaft of patent document 1, the rotational resistance caused by the bearing is eliminated. However, in this case, the axis of the spindle shaft is not fixed, and the spindle shaft cannot function as a spindle shaft.
The purpose of the present invention is to provide a structure capable of efficiently transmitting power in a transmission.
[ means for solving problems ]
A transmission of an embodiment of the present invention includes: a sun gear (sun roller) that rotates about a central axis; a plurality of planetary rotating bodies arranged around the sun gear; a carrier (carrier) that maintains the plurality of planetary rotating bodies in a state of being spaced apart from each other, and supports the plurality of planetary rotating bodies to be rotatable and revolvable with respect to the central shaft; an inner ring (inner ring) located outward of the center of the planetary rotor with respect to the central axis in a radial direction of the sun gear; a case (casting) holding the inner ring; and a shaft body that rotates together with the carrier around the central axis.
The plurality of planetary rotors includes: a plurality of 1 st planetary rotors located on one side in an axial direction of the sun gear; and a plurality of 2 nd planetary rotating bodies located on the other side than the plurality of 1 st planetary rotating bodies in the axial direction. The carrier rotates around the central axis together with the revolution of the plurality of planetary rotating bodies. The inner ring includes: an intermediate ring that is located between the plurality of 1 st planetary rotating bodies and the plurality of 2 nd planetary rotating bodies in the axial direction, and that contacts the plurality of 1 st planetary rotating bodies and the plurality of 2 nd planetary rotating bodies; and a pressing portion that presses the plurality of 1 st planetary rotating members and the plurality of 2 nd planetary rotating members and the sun gear against each other, and presses the plurality of 1 st planetary rotating members and the plurality of 2 nd planetary rotating members and the intermediate ring against each other. The 1 st planetary rotating bodies and the 2 nd planetary rotating bodies are supported by a carrier which is connected into a whole.
[ Effect of the invention ]
According to the transmission of the embodiment of the present invention, power can be transmitted efficiently.
Drawings
Fig. 1 is a diagram showing a schematic configuration of a drive unit including a transmission according to an embodiment of the present invention.
Fig. 2 is a sectional view taken along line II-II of fig. 1.
Fig. 3 is a view of the plurality of 1 st planetary rotating bodies and the plurality of 2 nd planetary rotating bodies as viewed from one side toward the other side in the axial direction.
Fig. 4 is a view showing another example of the plurality of 1 st planetary rolling elements and the plurality of 2 nd planetary rolling elements when viewed from one side to the other side in the axial direction.
Fig. 5 is a diagram showing a schematic configuration of a drive unit including a transmission according to another embodiment of the present invention.
Fig. 6 is a view showing another example of the planetary rolling bodies.
Fig. 7 is a view showing still another example of the planetary rolling bodies.
Detailed Description
Embodiments of the present invention will be described below with reference to the drawings. The dimensions of the constituent members in the drawings do not faithfully represent the actual dimensions of the constituent members, the dimensional ratios of the constituent members, and the like. In the following description, the term "axial" refers to the "axial direction" of the sun gear, the term "radial" refers to the "radial direction" of the sun gear, and the term "circumferential direction" refers to the "circumferential direction" of the sun gear. In addition, when simply described as "one side" is referred to as a plurality of 1 st planetary rotation element sides in the axial direction of the sun gear with reference to the intermediate ring, and when simply described as "the other side" is referred to as a plurality of 2 nd planetary rotation element sides in the axial direction of the sun gear with reference to the intermediate ring.
(Overall Structure)
Fig. 1 is a diagram showing a schematic configuration of a drive unit 100 including a transmission 10 according to an embodiment of the present invention. Fig. 2 is a sectional view taken along line II-II of fig. 1.
Referring to fig. 1, a drive unit 100 includes a transmission 10 and a motor 50. First, the motor 50 will be explained. The transmission 10 of the present embodiment can be used in combination with various known motors. Therefore, the motor 50 will be briefly described.
The motor 50 is an outer rotor (outer rotor) type motor. In the present embodiment, the motor 50 is a hollow cup motor (core motor). In fig. 1, the motor 50 is shown in a simplified manner. The motor 50 includes a rotor 51, a commutator 52, a magnet (magnet)53, a support member 54, a frame 55, and a lid 56.
Although detailed description is omitted, the rotor 51 includes a cylindrical coil (coil) and a holder (holder) for holding the coil. In the present embodiment, a sun gear 1, which will be described later, of the transmission 10 is fixed to a carrier of the rotor 51. That is, in the present embodiment, the sun gear 1 is used as the output shaft of the motor 50. The commutator 52 has a cylindrical shape. In the present embodiment, the sun gear 1 is fixed to the rotor 51 through the inside of the commutator 52. The sun gear 1, the rotor 51, and the commutator 52 rotate integrally.
The frame 55 has a cylindrical housing portion 55a extending in the axial direction, a hollow disk-shaped bottom portion 55b, a cylindrical protruding portion 55c, and a hollow disk-shaped bottom portion 55 d. The bottom portion 55b extends radially inward from one end portion of the receiving portion 55a in the axial direction. The diameter of the bottom portion 55b is larger than the diameter of a later-described support portion 3c of the transmission 10. The bottom portion 55b functions as a restricting portion that restricts movement of a pressing portion 45, which will be described later, of the transmission 10. The protruding portion 55c protrudes from the inner peripheral portion of the bottom portion 55b toward one side in the axial direction. The protruding portion 55c is inserted into a support portion 3c of the transmission 10, which will be described later. The protruding portion 55c functions as a support portion that rotatably supports a rotary member 3, which will be described later, of the transmission 10. The bottom portion 55d extends radially inward from one end portion of the protrusion 55c in the axial direction. In the present embodiment, the sun gear 1 penetrates the bottom portion 55 d.
The magnet 53 is fixed to the support member 54 inside the rotor 51. The support member 54 is fixed to the lid 56. The cover 56 is fixed to the other end portion of the frame 55 in the axial direction. Thereby, the magnet 53 is fixed to the frame 55. Although not shown, a lead wire or the like for supplying current to the motor 50 is also provided in the frame 55 as appropriate.
Next, the transmission 10 will be explained. The transmission 10 includes a sun gear 1, a plurality of 1 st planetary rolling elements 2a, a plurality of 2 nd planetary rolling elements 2b, a rotating member 3, an inner ring 4, and a case 5.
The sun gear 1 rotates about a central axis C. In the present embodiment, the sun gear 1 is an output shaft of the motor 50. The outer peripheral surface of the sun gear 1 has a recess 1a and a recess 1 b. Referring to fig. 1 and 2, the recess 1a extends over the entire circumference of the outer peripheral surface of the sun gear 1. Referring to fig. 1, similarly, the concave portion 1b extends over the entire circumference of the outer peripheral surface of the sun gear 1. The recess 1a and the recess 1b are spaced from each other in the axial direction of the sun gear 1. In the present embodiment, the recess 1a is located on one side of the sun gear 1 in the axial direction. When viewed in the radial direction of the sun gear 1, the concave portions 1a and 1b are curved in an arc shape so as to be recessed toward the central axis C. In other words, in the cross section of the sun gear 1 that passes through the central axis C and extends in the axial direction, the concave portions 1a and 1b are curved in an arc shape so as to be recessed toward the central axis C.
Referring to fig. 1 and 2, a plurality of 1 st planetary rotating bodies 2a are arranged around the sun gear 1. Referring to fig. 2, in the present embodiment, three 1 st planetary rotating bodies 2a are arranged around the sun gear 1. Referring to fig. 1, a plurality of 2 nd planetary rotating bodies 2b are arranged around a sun gear 1. In the present embodiment, three 2 nd planetary rotating bodies 2b are arranged around the sun gear 1, as in the 1 st planetary rotating body 2 a.
The 1 st planetary rolling bodies 2a are rotatable about a 1 st rotation axis R1 parallel to the central axis C. The plurality of 2 nd planetary rolling bodies 2b are rotatable about 2 nd rotation shafts R2 parallel to the central axis C, respectively. Each of the 1 st planetary rolling bodies 2a has a circular shape in a cross section perpendicular to the 1 st rotation axis R1. Similarly, each of the plurality of 2 nd planetary rolling bodies 2b has a circular shape in a cross section perpendicular to the 2 nd rotation axis R2. In the present embodiment, each of the plurality of 1 st planetary rolling elements 2a and the plurality of 2 nd planetary rolling elements 2b is a sphere. The diameters of the plurality of 1 st planetary rolling bodies 2a and the diameters of the plurality of 2 nd planetary rolling bodies 2b are equal to each other.
In the present embodiment, of the plurality of 1 st planetary rolling members 2a and the plurality of 2 nd planetary rolling members 2b, the plurality of 1 st planetary rolling members 2a are located on one side in the axial direction, and the plurality of 2 nd planetary rolling members 2b are located on the other side in the axial direction. The positions of the plurality of 1 st planetary rotating bodies 2a in the axial direction are equal to each other, and the positions of the plurality of 2 nd planetary rotating bodies 2b in the axial direction are equal to each other. The plurality of 1 st planetary rotating bodies 2a contact the sun gear 1 at the concave portions 1a, and the plurality of 2 nd planetary rotating bodies 2b contact the sun gear 1 at the concave portions 1 b. In the present embodiment, each of the 1 st planetary rolling members 2a contacts the concave portion 1a at a portion where the diameter of the cross section perpendicular to the 1 st rotation axis R1 becomes maximum (hereinafter referred to as the maximum diameter portion of the 1 st planetary rolling member 2 a). Each of the 2 nd planetary rolling members 2b contacts the concave portion 1b at a portion where the diameter of the cross section perpendicular to the 2 nd rotation axis R2 becomes maximum (hereinafter, referred to as the maximum diameter portion of the 2 nd planetary rolling member 2 b). In the 1 st planetary rolling element 2a shown in fig. 1, the central portion in the axial direction is the largest diameter portion. In addition, in the 2 nd planetary rolling body 2b shown in fig. 1, the central portion in the axial direction is the largest diameter portion.
The rotation member 3 includes a hollow carrier 3a, a solid shaft 3b, and a cylindrical support portion 3 c. In the axial direction, the shaft body 3b is located on one side of the carriage 3a, and the support portion 3c is located on the other side of the carriage 3 a.
The carriage 3a, the shaft 3b, and the support 3C are rotatable about the central axis C. In the present embodiment, the carriage 3a, the shaft 3b, and the support portion 3c are integrated. Therefore, the shaft body 3b and the support portion 3C rotate together with the carriage 3a around the central axis C.
The carrier 3a supports the plurality of 1 st planetary rolling elements 2a and the plurality of 2 nd planetary rolling elements 2b while maintaining a spaced state. The carrier 3a supports the plurality of 1 st planetary rolling elements 2a and the plurality of 2 nd planetary rolling elements 2b so as to be rotatable and revolvable about the central axis C. In the present embodiment, the 1 st planetary rolling element 2a rotates about the 1 st rotation axis R1 and revolves about the central axis C. The 2 nd planetary rolling element 2b rotates about the 2 nd rotation axis R2 and revolves about the central axis C. The carriage 3a will be specifically described below.
Referring to fig. 1 and 2, the carrier 3a has an insertion hole 31 in its axial center. The sun gear 1 is rotatably inserted into the insertion hole 31.
Referring to fig. 1, the carrier 3a includes a plurality of receiving portions 32a that receive the plurality of 1 st planetary rotating bodies 2a and a plurality of receiving portions 32b that receive the plurality of 2 nd planetary rotating bodies 2 b. The plurality of receiving portions 32a and the plurality of receiving portions 32a of the plurality of receiving portions 32b are located on one side in the axial direction, and the plurality of receiving portions 32b are located on the other side in the axial direction.
Referring to fig. 1 and 2, the accommodating portion 32a penetrates the carrier 3a in the radial direction, and has openings on the inner circumferential surface and the outer circumferential surface of the carrier 3a, respectively. The 1 st planetary rolling element 2a accommodated in the accommodating portion 32a projects radially inward from the opening on the inner peripheral surface side and radially outward from the opening on the outer peripheral surface side. The portion of the 1 st planetary rotating body 2a projecting radially inward contacts the sun gear 1, and the portion projecting radially outward contacts the inner ring 4. In the present embodiment, as described above, the portion of the 1 st planetary rotating body 2a that protrudes radially inward contacts the concave portion 1a of the sun gear 1. The contact between the 1 st planetary rolling element 2a and the inner ring 4 will be described later.
Referring to fig. 2, the plurality of receiving portions 32a are arranged at regular intervals in the circumferential direction. Thereby, the plurality of 1 st planetary rotating bodies 2a are supported by the carrier 3a at regular intervals in the circumferential direction. In the present embodiment, the three receiving portions 32a are arranged at intervals of 120 ° in the circumferential direction. Thereby, the three 1 st planetary rotating bodies 2a are supported by the carrier 3a at intervals of 120 ° in the circumferential direction.
Referring to fig. 1, the receiving portion 32b radially penetrates the carrier 3a, and has openings on the inner and outer circumferential surfaces of the carrier 3a, as in the case of the receiving portion 32 a. The 2 nd planetary rolling element 2b accommodated in the accommodating portion 32b projects radially inward from the opening on the inner peripheral surface side and radially outward from the opening on the outer peripheral surface side. The radially inwardly projecting portion of the 2 nd planetary rotating body 2b contacts the sun gear 1, and the radially outwardly projecting portion contacts the inner ring 4. In the present embodiment, as described above, the portion of the 2 nd planetary rotating body 2b that protrudes radially inward contacts the concave portion 1b of the sun gear 1. The contact between the 2 nd planetary rolling bodies 2b and the inner ring 4 will be described later.
Although not shown, the plurality of receiving portions 32b are arranged at regular intervals in the circumferential direction, as in the plurality of receiving portions 32 a. Thereby, the plurality of 2 nd planetary rotating bodies 2b are also supported at the carrier 3a at regular intervals in the circumferential direction. In the present embodiment, the three receiving portions 32b are arranged at intervals of 120 ° in the circumferential direction. Thereby, the three 2 nd planetary rotating bodies 2b are supported at intervals of 120 ° in the circumferential direction on the carrier 3 a.
In the present embodiment, the plurality of 1 st planetary rotating bodies 2a are supported by the carrier 3a in a state in which movement in the circumferential direction with respect to the carrier 3a is restricted (i.e., in a state in which relative movement between the 1 st planetary rotating bodies 2a and the carrier 3a in the circumferential direction is restricted). Similarly, the plurality of 2 nd planetary rotating bodies 2b are supported by the carrier 3a in a state in which movement in the circumferential direction with respect to the carrier 3a is restricted (i.e., in a state in which relative movement between the 2 nd planetary rotating bodies 2b and the carrier 3a in the circumferential direction is restricted). Therefore, the carrier 3a rotates about the central axis C together with the revolution of the plurality of 1 st planetary rotating bodies 2a and the plurality of 2 nd planetary rotating bodies 2 b. In the present embodiment, the carrier 3a rotates around the central axis C in accordance with the revolution of the plurality of 1 st planetary rolling elements 2a and the plurality of 2 nd planetary rolling elements 2 b.
The carriage 3a is a member integrally connected. In other words, the portion of the carrier 3a that supports the plurality of 1 st planetary rotating bodies 2a is integrated with the portion that supports the plurality of 2 nd planetary rotating bodies 2 b. Therefore, the plurality of 1 st planetary rolling bodies 2a and the plurality of 2 nd planetary rolling bodies 2b revolve at the same time.
Fig. 3 is a view of the plurality of 1 st planetary rotating bodies 2a and the plurality of 2 nd planetary rotating bodies 2b as viewed from one side toward the other side in the axial direction. In fig. 3, the position of the center axis C is indicated by a chain line. In fig. 3, the orbit O of the center (the 1 st rotation axis R1) of the 1 st planetary rolling element 2a when the 1 st planetary rolling element 2a revolves is indicated by a two-dot chain line. Although not shown, the orbit of the center (the 2 nd rotation axis R2) of the 2 nd planetary rotation body 2b when the 2 nd planetary rotation body 2b revolves coincides with the orbit O when viewed from the one side to the other side.
Referring to fig. 3, in the present embodiment, when the other side is viewed from one side in the axial direction, the center position of the 1 st planetary rolling member 2a coincides with the center position of the 2 nd planetary rolling member 2 b. In other words, when the other side is viewed from one side in the axial direction, the positions of the plurality of 1 st planetary rotating bodies 2a coincide with the positions of the plurality of 2 nd planetary rotating bodies 2b in the circumferential direction.
In the radial direction, the distance between the central axis C and the center of each 1 st planetary rolling element 2a (1 st rotation axis R1) and the distance between the central axis C and the center of each 2 nd planetary rolling element 2b (2 nd rotation axis R2) are equal to each other. In other words, when the plurality of 1 st planetary rolling members 2a and the plurality of 2 nd planetary rolling members 2b revolve, the diameter of the orbit O of the center (1 st rotation axis R1) of the 1 st planetary rolling members 2a is equal to the diameter of the orbit of the center (2 nd rotation axis R2) of the 2 nd planetary rolling members 2 b.
In addition, as shown in fig. 4, when the other side is viewed from one side in the axial direction, the positions of the plurality of 1 st planetary rolling members 2a and the plurality of 2 nd planetary rolling members 2b may be shifted in the circumferential direction. Specifically, for example, the positions of the plurality of 1 st planetary rolling elements 2a and the positions of the plurality of 2 nd planetary rolling elements 2b may be shifted by 60 ° in the circumferential direction.
Referring to fig. 1, the shaft body 3b extends from the carrier 3a toward one side in the axial direction. The cylindrical support portion 3c extends from the carrier 3a toward the other side in the axial direction. The inner peripheral surface of the support portion 3c has a diameter larger than that of the insertion hole 31. In the support portion 3c, a protruding portion 55c of the frame 55 of the motor 50 is inserted. In the present embodiment, the support portion 3c is rotatably supported by the protruding portion 55 c.
The inner ring 4 is located radially outward of the center of the 1 st planetary rolling element 2a and the center of the 2 nd planetary rolling element 2b with respect to the central axis C. The inner ring 4 is held in the housing 5. The inner ring 4 has an intermediate ring 40, a 1 st ring portion 41, a 2 nd ring portion 42, and a pressing portion 45. The intermediate ring 40 and the 1 st ring portion 41 contact the plurality of 1 st planetary rolling elements 2a, and the intermediate ring 40 and the 2 nd ring portion 42 contact the plurality of 2 nd planetary rolling elements 2 b.
Referring to fig. 1 and 2, the 1 st ring portion 41 is located on one side of the plurality of 1 st planetary rotating bodies 2a in the axial direction. The 1 st ring part 41 is disposed coaxially with the sun gear 1. The 1 st ring part 41 has an inclined surface 41a extending annularly over the entire circumference of the 1 st ring part 41. The inclined surface 41a has a circular shape in a cross section perpendicular to the axial direction. Referring to fig. 1, the diameter of the inclined surface 41a in the vertical section gradually increases from one side toward the other side in the axial direction. In other words, the inclined surface 41a is inclined toward the other side in the axial direction. In the present embodiment, the inclined surface 41a is a part of a truncated cone having a generatrix extending in the tangential direction of the 1 st planetary rotating body 2a at a contact point with the 1 st planetary rotating body 2 a. The inclined surface 41a faces the plurality of 1 st planetary rolling bodies 2 a. The inclined surface 41a contacts the plurality of 1 st planetary rotating bodies 2 a. In the present embodiment, the inclined surface 41a extends linearly on a cross section (cross section shown in fig. 1) that passes through the central axis C and extends in the axial direction. The inclined surface 41a may be curved in the cross section shown in fig. 1. For example, the inclined surface 41a may be a curved surface curved in an arc shape, similarly to the inclined surface 46a of fig. 7 described later.
Referring to fig. 1, the 2 nd ring portion 42 is located on the other side of the plurality of 2 nd planetary rotating bodies 2b in the axial direction. The 2 nd ring part 42 is disposed coaxially with the sun gear 1. The 2 nd ring part 42 has an inclined surface 42a extending annularly over the entire circumference of the 2 nd ring part 42. The inclined surface 42a has a circular shape in a cross section perpendicular to the axial direction. The diameter of the inclined surface 42a in the vertical section gradually increases from the other side toward one side in the axial direction. In other words, the inclined surface 42a is inclined toward one of the sides in the axial direction. In the present embodiment, the inclined surface 42a is a part of a truncated cone having a generatrix extending in the tangential direction of the 2 nd planetary rotor 2b at a contact point with the 2 nd planetary rotor 2 b. The inclined surface 42a faces the plurality of 2 nd planetary rolling bodies 2 b. The inclined surface 42a contacts the plurality of 2 nd planetary rotating bodies 2 b. In the present embodiment, the inclined surface 42a extends linearly in the cross section shown in fig. 1. The inclined surface 42a may be curved in the cross section shown in fig. 1, similarly to the inclined surface 41 a.
The intermediate ring 40 is located between the plurality of 1 st planetary rolling elements 2a and the plurality of 2 nd planetary rolling elements 2b in the axial direction, and contacts the plurality of 1 st planetary rolling elements 2a and the plurality of 2 nd planetary rolling elements 2 b. In the present embodiment, the intermediate ring 40 includes the 3 rd ring part 43 and the 4 th ring part 44. The intermediate ring 40 (the 3 rd ring part 43 and the 4 th ring part 44) is disposed coaxially with the sun gear 1.
The 3 rd ring part 43 is positioned at the other side of the plurality of 1 st planetary rotating bodies 2a and at one side of the 4 th ring part 44 in the axial direction. The 3 rd ring part 43 has an inclined surface 43a extending annularly over the entire circumference of the 3 rd ring part 43. The inclined surface 43a has a circular shape in a cross section perpendicular to the axial direction. The diameter of the inclined surface 43a in the vertical section gradually increases from the other side toward one side in the axial direction. In other words, the inclined surface 43a is inclined toward one of the sides in the axial direction. In the present embodiment, the inclined surface 43a is a part of a truncated cone having a generatrix extending in the tangential direction of the 1 st planetary rotating body 2a at a contact point with the 1 st planetary rotating body 2 a. The inclined surface 43a faces the plurality of 1 st planetary rolling bodies 2 a. The inclined surface 43a contacts the plurality of 1 st planetary rotating bodies 2 a. In the present embodiment, the inclined surface 43a extends linearly in the cross section shown in fig. 1. The inclined surface 43a may be curved in the cross section shown in fig. 1, similarly to the inclined surface 41 a.
The 4 th annulus 44 is located on one side of the plurality of 2 nd planetary rotating bodies 2b and on the other side of the 3 rd annulus 43 in the axial direction. The 4 th ring part 44 has an inclined surface 44a extending annularly over the entire circumference of the 4 th ring part 44. The inclined surface 44a has a circular shape in a cross section perpendicular to the axial direction. The inclined surface 44a in the vertical section gradually expands in diameter from one side toward the other side in the axial direction. In other words, the inclined surface 44a is inclined toward the other side in the axial direction. In the present embodiment, the inclined surface 44a is a part of a truncated cone having a generatrix extending in the tangential direction of the 2 nd planetary rotor 2b at a contact point with the 2 nd planetary rotor 2 b. The inclined surface 44a faces the plurality of 2 nd planetary rolling elements 2 b. The inclined surface 44a contacts the plurality of 2 nd planetary rotating bodies 2 b. In the present embodiment, the inclined surface 44a extends linearly in the cross section shown in fig. 1. The inclined surface 44a may be curved in the cross section shown in fig. 1, similarly to the inclined surface 41 a.
In the present embodiment, the 3 rd ring part 43 and the 4 th ring part 44 are independent members. However, the 3 rd ring part 43 and the 4 th ring part 44 may be integrally connected. That is, the 3 rd ring part 43 and the 4 th ring part 44 may be formed integrally as one member.
The pressing portion 45 is located on the other side of the 2 nd ring portion 42 in the axial direction. As the pressing portion 45, for example, an elastic member can be used. In the present embodiment, a coil spring (coil spring) is used as the pressing portion 45. The pressing portion 45 is disposed coaxially with the sun gear 1 and the carriage 3 a.
The pressing portion 45 contacts the 2 nd ring portion 42 from the other side in the axial direction to press the 2 nd ring portion 42 to one side in the axial direction. In the present embodiment, the bottom portion 55b of the frame 55 of the motor 50 is located on the other side of the pressing portion 45 in the axial direction. Specifically, the bottom portion 55b supports the other end portion of the pressing portion 45 in the axial direction. Thereby, the movement of the pressing portion 45 toward the other side in the axial direction is restricted.
The pressing portion 45 presses the plurality of 1 st planetary rolling members 2a and the intermediate ring 40 against each other, and presses the plurality of 2 nd planetary rolling members 2b and the intermediate ring 40 against each other. The pressing portion 45 presses the plurality of 1 st planetary rotating bodies 2a and the sun gear 1 against each other, and presses the plurality of 2 nd planetary rotating bodies 2b and the sun gear 1 against each other. Further, the pressing portion 45 presses the plurality of 1 st planetary rolling members 2a and the 1 st ring portion 41 against each other, and presses the plurality of 2 nd planetary rolling members 2b and the 2 nd ring portion 42 against each other. The relationship among the sun gear 1, the plurality of 1 st planetary rolling elements 2a, the plurality of 2 nd planetary rolling elements 2b, and the inner ring 4 will be specifically described below.
In the present embodiment, the 2 nd ring part 42 is pressed toward one of the sides in the axial direction by the pressing part 45, whereby the plurality of 2 nd planetary rotating bodies 2b are pressed toward the one of the sides and the radially inner side. The plurality of 2 nd planetary rotating bodies 2b are pressed toward the one side, whereby the intermediate ring 40 is pressed toward the one side. The intermediate ring 40 is pressed toward the one side, whereby the plurality of 1 st planetary rotating bodies 2a are pressed toward the one side and the radially inner side. The plurality of 1 st planetary rotating bodies 2a are pressed toward the one side, whereby the 1 st ring portion 41 is pressed toward the one side. Further, the movement of the 1 st ring portion 41 toward the one side is restricted by a restricting portion 5b of the housing 5, which will be described later.
As described above, the 2 nd ring portion 42 contacts the plurality of 2 nd planetary rotating bodies 2b on the inclined surface 42 a. Thereby, a normal force acts on each 2 nd planetary rolling element 2b from the inclined surface 42 a. Further, the intermediate ring 40 contacts the plurality of 2 nd planetary rolling bodies 2b on the inclined surface 44 a. Thereby, a normal force acts on each 2 nd planetary rolling element 2b from the inclined surface 44 a. As a result of these actions, the plurality of 2 nd planetary rotating bodies 2b can be pressed against the sun gear 1 with a sufficient force. This enables power to be efficiently transmitted between the sun gear 1 and the plurality of 2 nd planetary rotating bodies 2 b.
Further, the intermediate ring 40 contacts the plurality of 1 st planetary rolling bodies 2a on the inclined surface 43 a. Thereby, a normal force acts on each 1 st planetary rotation body 2a from the inclined surface 43 a. The 1 st ring portion 41 contacts the plurality of 1 st planetary rolling elements 2a on the inclined surface 41 a. Thereby, a normal force acts on each 1 st planetary rolling element 2a from the inclined surface 41 a. As a result of these actions, the plurality of 1 st planetary rotating bodies 2a can be pressed with a sufficient force toward the sun gear 1. This enables power to be efficiently transmitted between the sun gear 1 and the plurality of 1 st planetary rotating bodies 2 a.
The housing 5 has: a cylindrical portion 5a extending in the axial direction; a hollow substantially disc-shaped restriction portion 5b extending radially inward from one axial end of the cylindrical portion 5 a; and a cylindrical support portion 5c protruding from an inner peripheral portion of the restricting portion 5b toward one of the sides in the axial direction.
The cylindrical portion 5a accommodates the sun gear 1, the plurality of 1 st planetary rotating bodies 2a, the plurality of 2 nd planetary rotating bodies 2b, the carrier 3a of the rotating member 3, and the inner ring 4. In the present embodiment, a part of the sun gear 1 protrudes from the cylindrical portion 5a toward the other side in the axial direction. The other side of the cylindrical portion 5a in the axial direction is fixed to a frame 55 of the motor 50.
An intermediate ring 40, a 1 st ring part 41 and a 2 nd ring part 42 are attached to the inner peripheral surface of the cylindrical part 5 a. In the present embodiment, the intermediate ring 40, the 1 st ring part 41, and the 2 nd ring part 42 are attached to the cylindrical part 5a in a state of being movable in the axial direction and being restricted from moving in the circumferential direction of the cylindrical part 5a with respect to the cylindrical part 5 a.
As described above, in the present embodiment, the movement of the intermediate ring 40, the 1 st ring part 41, and the 2 nd ring part 42 in the circumferential direction is restricted. This allows the plurality of 1 st planetary rolling elements 2a and the plurality of 2 nd planetary rolling elements 2b to smoothly revolve around the central axis C.
The restricting portion 5b restricts the movement of the 1 st ring portion 41 toward one side in the axial direction as described above. The support portion 5c rotatably supports the shaft body 3 b. Although not shown, an O-ring, for example, may be provided between the shaft body 3b and the support portion 5 c. At this time, by the frictional resistance of the O-ring, when the rotary member 3 is stopped, or when a force acts on the rotary member 3 from the outside, backlash (backlash) can be suppressed.
In the drive unit 100, when the sun gear 1 is rotated by the driving force of the motor 50, the plurality of 1 st planetary rolling elements 2a and the plurality of 2 nd planetary rolling elements 2b rotate and revolve around the central axis C. The carrier 3a rotates about the central axis C by the revolution of the plurality of 1 st planetary rolling elements 2a and the plurality of 2 nd planetary rolling elements 2 b. Thereby, the shaft body 3b rotates about the central axis C. In this way, the rotation of the sun gear 1 is decelerated and transmitted to the shaft body 3 b.
Here, in the transmission 10, the plurality of 1 st planetary rotation members 2a and the plurality of 2 nd planetary rotation members 2b are pressed against the sun gear 1 by the pressing portions 45 of the inner ring 4. The transmission 10 further includes an intermediate ring 40 between the plurality of 1 st planetary rotating bodies 2a and the plurality of 2 nd planetary rotating bodies 2 b. The intermediate ring 40 restricts the positions of the 1 st planetary rolling elements 2a and the 2 nd planetary rolling elements 2b in the axial direction. Thus, when the sun gear 1 rotates, the contact state between the plurality of 1 st planetary rolling elements 2a and the sun gear 1 and the contact state between the plurality of 2 nd planetary rolling elements 2b and the sun gear 1 can be maintained. This enables power (rotation) to be efficiently transmitted from the sun gear 1 to the shaft body 3 b.
In the transmission 10, the plurality of 1 st planetary rolling members 2a and the plurality of 2 nd planetary rolling members 2b are arranged at different positions in the axial direction. At this time, the plurality of 1 st planetary rolling elements 2a and the plurality of 2 nd planetary rolling elements 2b provided for transmitting power can be used as bearings for rotatably supporting the sun gear 1. Thus, compared to a case where a bearing for supporting the sun gear 1 is provided independently of the plurality of 1 st planetary rolling elements 2a and the plurality of 2 nd planetary rolling elements 2b, the bearing can be omitted, and therefore, the loss of power transmitted between the sun gear 1 and the shaft body 3b can be reduced. As a result, power can be efficiently transmitted between the sun gear 1 and the shaft body 3 b. Further, since no separate bearing is required, the transmission 10 can be configured in a small size. In particular, in the present embodiment, the plurality of 1 st planetary rotating bodies 2a contact the sun gear 1 at the concave portions 1a, and the plurality of 2 nd planetary rotating bodies 2b contact the sun gear 1 at the concave portions 1 b. This enables the sun gear 1 to be positioned both in the axial direction and in the radial direction.
In the transmission 10, power can be transmitted from the sun gear 1 to the shaft body 3b through the plurality of 1 st planetary rotating bodies 2a and the plurality of 2 nd planetary rotating bodies 2 b. At this time, the power transmission capability from the sun gear 1 to the shaft body 3b can be doubled as compared with the case where the power is transmitted only by any one of the plurality of 1 st planetary rotating bodies 2a and the plurality of 2 nd planetary rotating bodies 2 b. This can sufficiently increase the capacity of the drive unit 100.
In the transmission 10, the 1 st planetary rotating body 2a contacts the sun gear 1 at the concave portion 1a, and the 2 nd planetary rotating body 2b contacts the sun gear 1 at the concave portion 1 b. In this case, the contact area between the 1 st planetary rolling element 2a and the sun gear 1 and the contact area between the 2 nd planetary rolling element 2b and the sun gear 1 can be increased. Thus, local generation of large stress can be suppressed at the contact portion between the 1 st planetary rolling element 2a and the sun gear 1 and the contact portion between the 2 nd planetary rolling element 2b and the sun gear 1. As a result, damage to the sun gear 1, the 1 st planetary rolling element 2a, and the 2 nd planetary rolling element 2b can be suppressed.
In the transmission 10, the positions of the intermediate ring 40, the 1 st ring member 41, and the 2 nd ring member 42 in the axial direction are restricted by the restricting portions 5 b. Thereby, the plurality of 1 st planetary rolling bodies 2a and the plurality of 2 nd planetary rolling bodies 2b are positioned. As a result, the movement of the sun gear 1 in the axial direction is restricted. This facilitates positioning of the sun gear 1.
In the transmission 10, each of the 1 st planetary rotating bodies 2a contacts the concave portion 1a at the maximum diameter portion. This enables the plurality of first planetary rolling bodies 2a to be more appropriately pressed toward the sun gear 1. As a result, power can be efficiently transmitted between the sun gear 1 and the plurality of 1 st planetary rotating bodies 2 a. The same applies to the relationship between the plurality of 2 nd planetary rolling elements 2b and the concave portions 1 b.
(other embodiments)
Fig. 5 is a diagram showing a schematic configuration of a drive unit 100a including a transmission 10a according to another embodiment of the present invention. The driving unit 100a is different from the driving unit 100 in that: a transmission 10a instead of the transmission 10; and a motor 60 instead of the motor 50.
The transmission 10a differs from the transmission 10 in that: a sun gear 11 in place of the sun gear 1; and a housing 15 instead of the housing 5. The sun gear 11 has the same structure as the sun gear 1 except that the length in the axial direction is shorter than that of the sun gear 1. The shape of the housing may be changed as appropriate depending on the structure of the motor, and therefore, a detailed description of the housing 15 is omitted.
As the structure of the motor 60, various well-known motor structures can be used, and thus detailed description is omitted, but the motor 60 includes a stator (stator)60a and a rotor 60 b. The stator 60a is fixed to the outer peripheral surface of the housing 15. The rotor 60b includes: a bottomed cylindrical yoke (yoke)60 c; and a cylindrical magnet 60d fixed to the inner peripheral surface of the yoke 60 c. The rotor 60b is disposed so as to cover the outer periphery of the stator 60 a. The sun gear 11 is fixed to the yoke 60 c. Therefore, the sun gear 11 rotates integrally with the rotor 60 b.
In the drive unit 100a of the present embodiment, when the sun gear 11 is rotated by the driving force of the motor 60, the rotation of the sun gear 11 is decelerated and transmitted to the shaft body 3b, similarly to the drive unit 100. Here, in the present embodiment, since the stator 60a is provided on the outer peripheral surface of the housing 15, the dimension of the drive unit 100a in the radial direction is larger than the dimension of the drive unit 100 in the radial direction. However, the dimension of the drive unit 100a in the axial direction can be made smaller than the dimension of the drive unit 100 in the axial direction.
(further embodiments)
In the above-described embodiment, the case where the sun gear is used as the output shaft of the motor has been described, but the sun gear and the output shaft of the motor may be integrated or may be separate bodies. That is, the motor may have an output shaft independently of the sun gear. At this time, the sun gear is fixed to the output shaft of the motor, and the sun gear and the output shaft of the motor rotate integrally.
In the above embodiment, the case where the motor drives the sun gear to rotate has been described, but the motor may drive the shaft body 3b to rotate. At this time, the rotation of the shaft body 3b is accelerated and transmitted to the sun gear 1 or the sun gear 11. That is, the transmission functions as an accelerator. When the transmission is used as an accelerator, the shaft body 3b may be integrated with the output shaft of the motor or may be separate. That is, the shaft body 3b may be used as an output shaft of the motor, or the motor may have an output shaft independently of the shaft body 3 b. When the shaft body 3b and the output shaft of the motor are separate bodies, the shaft body 3b and the output shaft of the motor are fixed, and the shaft body 3b and the output shaft of the motor rotate integrally.
In the above embodiment, the case where the 1 st planetary rolling member 2a and the 2 nd planetary rolling member 2b are each a sphere has been described, but the shape of the planetary rolling members is not limited to the above example. Specifically, the planetary rolling bodies may have any shape as long as they can rotate around the central axis C and can revolve around the central axis C. Therefore, for example, a circular columnar planetary rolling member 2c as shown in fig. 6 may be used instead of the 1 st planetary rolling member 2 a. Although detailed description is omitted, the outer shape of the planetary rolling member 2c (more specifically, the shape of both end portions in the axial direction), the size/position of the 1 st ring portion 41, the size/position of the 3 rd ring portion 43, and the like may be appropriately adjusted so that the planetary rolling member 2c can be pressed toward the inside in the axial direction and the radial direction of the sun gear 12 by the inclined surfaces 41a, 43 a. Although not described in detail, the outer peripheral surface of the sun gear 12 has a concave portion into which the planetary rotation member 2c is fitted, similarly to the outer peripheral surface of the sun gear 1. Although not shown, the planetary rolling bodies 2c may be used in place of the 2 nd planetary rolling body 2 b.
The cylindrical planetary rolling member includes a so-called barrel-shaped planetary rolling member having a central portion with a larger diameter than both end portions in the axial direction. Therefore, for example, a planetary rolling element 2d shown in fig. 7 may be used instead of the 1 st planetary rolling element 2 a. Although detailed description is omitted, the size and position of the 1 st ring portion 46, the shape of the inclined surface 46a, the size and position of the 3 rd ring portion 47, the shape of the inclined surface 47a, and the like may be appropriately adjusted so that the planetary rotation body 2d can be pressed inward in the axial direction and the radial direction of the sun gear 13. Although not described in detail, the outer peripheral surface of the sun gear 13 has a concave portion into which the planetary rotation member 2d is fitted, similarly to the outer peripheral surface of the sun gear 1. Although not shown, the planetary rolling bodies 2d may be used in place of the 2 nd planetary rolling body 2 b.
In the above-described embodiment, the case where the plurality of planetary rolling members are arranged in two rows in the axial direction has been described, but the plurality of planetary rolling members may be arranged in three or more rows in the axial direction. In the above embodiment, the case where three planetary rolling members are arranged around the central axis C in each row has been described, but four or more planetary rolling members may be arranged.
[ industrial applicability ]
The present invention is applicable to a transmission and a drive unit including the transmission.
Claims (9)
1. A transmission, characterized by comprising:
a sun gear that rotates about a central axis;
a plurality of planetary rotating bodies arranged around the sun gear;
a carrier that maintains the plurality of planetary rotating bodies in a state of being spaced apart from each other, and supports the plurality of planetary rotating bodies so as to be rotatable and revolvable with respect to the central shaft;
an inner ring located outside the center of the planetary rotating body with respect to the central axis in the radial direction of the sun gear;
a housing holding the inner ring; and
a shaft body that rotates together with the carrier around the central axis,
the plurality of planetary rotors includes:
a plurality of 1 st planetary rotors located on one side in an axial direction of the sun gear; and
a plurality of 2 nd planetary rolling bodies located on the other side than the plurality of 1 st planetary rolling bodies in the axial direction,
the carrier rotates around the central axis together with the revolution of the plurality of planetary rotating bodies,
the inner ring includes:
an intermediate ring that is located between the plurality of 1 st planetary rotating bodies and the plurality of 2 nd planetary rotating bodies in the axial direction, and that contacts the plurality of 1 st planetary rotating bodies and the plurality of 2 nd planetary rotating bodies; and
a pressing portion that presses the plurality of 1 st planetary rotating members, the plurality of 2 nd planetary rotating members, and the sun gear against each other, and presses the plurality of 1 st planetary rotating members, the plurality of 2 nd planetary rotating members, and the intermediate ring against each other,
the 1 st planetary rotating bodies and the 2 nd planetary rotating bodies are supported by a carrier which is connected into a whole.
2. The transmission of claim 1, wherein:
the outer peripheral surface of the sun gear has a 1 st concave part and a 2 nd concave part extending over the entire periphery,
the 1 st recess and the 2 nd recess are spaced from each other in the axial direction,
in a cross section of the sun gear that passes through the center axis and extends in the axial direction, the 1 st concave portion and the 2 nd concave portion are each recessed toward the center axis,
the plurality of 1 st planetary rotating bodies contact the sun gear at the 1 st concave portion respectively,
the plurality of 2 nd planetary rotating bodies contact the sun gear at the 2 nd concave portions, respectively.
3. The transmission of claim 2, wherein:
the 1 st planetary rotation bodies each rotate about a 1 st rotation axis parallel to the central axis and have a circular shape in a cross section perpendicular to the 1 st rotation axis,
the plurality of 2 nd planetary rotation bodies each rotate about a 2 nd rotation axis parallel to the central axis and have a circular shape in a cross section perpendicular to the 2 nd rotation axis,
the 1 st planetary rotating bodies contact the 1 st concave portion at a portion where a diameter of a cross section perpendicular to the 1 st rotation axis is maximized,
the plurality of 2 nd planetary rolling elements contact the 2 nd concave portion at a portion where a diameter of a cross section perpendicular to the 2 nd rotation axis is maximized, respectively.
4. A transmission according to claim 2 or 3, wherein:
the plurality of planet rotating bodies are respectively a sphere,
the diameters of the plurality of planetary rotating bodies are equal to each other,
distances from the central shaft to respective centers of the plurality of planetary rotating bodies in a radial direction of the sun gear are equal to each other.
5. The transmission according to any one of claims 1 to 3, wherein:
the inner ring further comprises:
a 1 st annulus located on one side of the 1 st plurality of planetary rotors in the axial direction; and
a 2 nd ring portion located on the other side of the plurality of 2 nd planetary rotating bodies in the axial direction,
the intermediate ring includes:
a 3 rd ring part which is positioned at the other side of the 1 st planetary rotating bodies in the axial direction; and
a 4 th annulus located between the 3 rd annulus and the plurality of 2 nd planetary rotating bodies in the axial direction,
the 1 st ring part has an inclined surface which extends annularly over the entire circumference of the 1 st ring part, contacts the 1 st planetary rotating bodies, and is inclined toward the other side in the axial direction,
the 2 nd ring part has an inclined surface which extends annularly over the entire circumference of the 2 nd ring part, contacts the plurality of 2 nd planetary rotating bodies, and is inclined toward one side thereof in the axial direction,
the 3 rd ring part has an inclined surface which extends annularly over the entire circumference of the 3 rd ring part, contacts the 1 st planetary rotating bodies, and is inclined toward one side thereof in the axial direction,
the 4 th ring part has an inclined surface that extends annularly over the entire circumference of the 4 th ring part, contacts the plurality of 2 nd planetary rotating bodies, and is inclined toward the other side in the axial direction.
6. The transmission of claim 5, wherein:
the housing has a cylindrical portion extending in the axial direction,
the 1 st ring part, the 2 nd ring part, and the intermediate ring are attached to an inner peripheral surface of the cylindrical part in a state of being movable in the axial direction and being restricted from moving in a circumferential direction of the cylindrical part with respect to the cylindrical part.
7. The transmission of claim 5, wherein:
the pressing portion contacts the 2 nd ring portion from the other side in the axial direction to press the 2 nd ring portion toward one side thereof.
8. The transmission of claim 7, further comprising:
a restricting member that is located on the other side than the 2 nd ring part in the axial direction and restricts movement of the pressing part toward the other side,
the shell is provided with a limiting part which is positioned on one side of the 1 st ring part in the axial direction and limits the movement of the 1 st ring part towards one side.
9. A drive unit characterized by comprising:
the transmission of any one of claims 1 to 8; and
a motor that drives one of the sun gear and the shaft body to rotate.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016149141A JP6727058B2 (en) | 2016-07-29 | 2016-07-29 | Transmission and drive unit |
| JP2016-149141 | 2016-07-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107664185A CN107664185A (en) | 2018-02-06 |
| CN107664185B true CN107664185B (en) | 2020-04-03 |
Family
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710636873.5A Expired - Fee Related CN107664185B (en) | 2016-07-29 | 2017-07-31 | Transmission and drive unit |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6727058B2 (en) |
| CN (1) | CN107664185B (en) |
Citations (6)
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| CN202251737U (en) * | 2011-09-08 | 2012-05-30 | 江阴克威齿轮箱制造有限公司 | Speed reducer in double-planet structure |
| CN203130934U (en) * | 2013-03-25 | 2013-08-14 | 盐城市金洲机械制造有限公司 | Double-stage driving servo planetary reducer |
| CN203146716U (en) * | 2013-03-13 | 2013-08-21 | 上海盛运机械工程有限公司 | Planet gear reducer with two rows of planet gears |
| CN105570409A (en) * | 2014-10-29 | 2016-05-11 | 日本电产新宝株式会社 | Friction power transmission device |
| CN205371520U (en) * | 2016-01-22 | 2016-07-06 | 吉林大学 | Power drive system based on doublestage planet is arranged two and is kept off derailleur |
| CN105757185A (en) * | 2016-04-25 | 2016-07-13 | 袁廷华 | Speed reducer |
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|---|---|---|---|---|
| US3600976A (en) * | 1970-02-26 | 1971-08-24 | Gen Motors Corp | Friction drive mechanism |
| JPS5533716Y2 (en) * | 1975-10-21 | 1980-08-11 | ||
| JPS5439763A (en) * | 1977-09-02 | 1979-03-27 | Hitachi Ltd | Frictional transmission device |
| JPS58172358U (en) * | 1982-05-13 | 1983-11-17 | アスモ株式会社 | reduction gear |
| TWI235214B (en) * | 2002-06-18 | 2005-07-01 | Yung-Tung Chen | Transmission system |
| US20150072828A1 (en) * | 2013-09-11 | 2015-03-12 | Jeffrey A Reuter | Planetary Gearbox Transmission using Gear Bearings |
-
2016
- 2016-07-29 JP JP2016149141A patent/JP6727058B2/en active Active
-
2017
- 2017-07-31 CN CN201710636873.5A patent/CN107664185B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202251737U (en) * | 2011-09-08 | 2012-05-30 | 江阴克威齿轮箱制造有限公司 | Speed reducer in double-planet structure |
| CN203146716U (en) * | 2013-03-13 | 2013-08-21 | 上海盛运机械工程有限公司 | Planet gear reducer with two rows of planet gears |
| CN203130934U (en) * | 2013-03-25 | 2013-08-14 | 盐城市金洲机械制造有限公司 | Double-stage driving servo planetary reducer |
| CN105570409A (en) * | 2014-10-29 | 2016-05-11 | 日本电产新宝株式会社 | Friction power transmission device |
| CN205371520U (en) * | 2016-01-22 | 2016-07-06 | 吉林大学 | Power drive system based on doublestage planet is arranged two and is kept off derailleur |
| CN105757185A (en) * | 2016-04-25 | 2016-07-13 | 袁廷华 | Speed reducer |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107664185A (en) | 2018-02-06 |
| JP6727058B2 (en) | 2020-07-22 |
| JP2018017352A (en) | 2018-02-01 |
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