WO2018147120A1 - Structure de lubrification pour dispositif de transmission à trains épicycloïdaux - Google Patents

Structure de lubrification pour dispositif de transmission à trains épicycloïdaux Download PDF

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Publication number
WO2018147120A1
WO2018147120A1 PCT/JP2018/002818 JP2018002818W WO2018147120A1 WO 2018147120 A1 WO2018147120 A1 WO 2018147120A1 JP 2018002818 W JP2018002818 W JP 2018002818W WO 2018147120 A1 WO2018147120 A1 WO 2018147120A1
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WO
WIPO (PCT)
Prior art keywords
oil
bearing
gear
planetary
lubricating oil
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PCT/JP2018/002818
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English (en)
Japanese (ja)
Inventor
亮輔 淺井
圭宏 吉田
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武蔵精密工業株式会社
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Application filed by 武蔵精密工業株式会社 filed Critical 武蔵精密工業株式会社
Publication of WO2018147120A1 publication Critical patent/WO2018147120A1/fr

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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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating

Definitions

  • the present invention relates to a lubricating structure in a planetary transmission device used for a reduction gear or a speed increaser.
  • a gear case As a planetary transmission device, as disclosed in Patent Document 1 below, a gear case, a first transmission shaft and a second transmission shaft that are rotatably supported on both side walls of the gear case, and a first transmission shaft, respectively.
  • An eccentric shaft that rotates eccentrically around the axis of the first transmission shaft as the first transmission shaft rotates, a planetary gear that is rotatably supported by the eccentric shaft, a first transmission shaft mounted on the gear case,
  • a ring gear that is fixed coaxially and meshes with a planetary gear, and a motion conversion mechanism that converts the planetary motion of the planetary gear into a rotational motion and transmits it to a second transmission shaft are known.
  • the lubricating oil stored in the gear case is diffused around by rotation of the oil diffusion member attached to the second transmission shaft, and the diffused lubricating oil is transferred to the second transmission shaft.
  • a lubrication structure is adopted in which it is received by an oil guide path provided on the shaft and supplied to the lubricated part.
  • the oil transmission path is formed so as to be directed toward the rotation center of the second transmission shaft. Therefore, the lubricating oil caught in the oil guide passage must flow against the centrifugal force accompanying the rotation of the second transmission shaft. Therefore, the lubricating oil does not easily reach the part to be lubricated and it is difficult to achieve the desired lubrication.
  • the present invention has been made in view of such circumstances, and a planetary transmission device that can effectively lubricate a portion to be lubricated by effectively using lubricating oil diffused in a gear case by an oil diffusing member. It is an object of the present invention to provide a lubricating structure.
  • a gear case a transmission shaft rotatably supported by the gear case via a first bearing, an eccentric shaft integrally coupled to the transmission shaft, and the eccentric shaft A planetary gear supported on a peripheral wall of the shaft via a second bearing; and a ring gear fixed to the gear case coaxially with the transmission shaft, wherein one side wall of the eccentric shaft faces the first bearing.
  • a lubricating structure in a planetary transmission device wherein the lubricating oil stored in the bottom of the gear case, an oil diffusion member for diffusing the lubricating oil into the gear case, and the first bearing opposite to the eccentric shaft Provided in the gear case so as to be adjacent to the side surface on the side, provided in the oil reservoir chamber for receiving the diffused lubricating oil, and provided in the eccentric shaft so as to penetrate between the one side wall and the peripheral wall, That the sump chamber and a fluid path for supplying lubricating oil having passed through the first bearing to the second bearing and the first feature.
  • the transmission shaft corresponds to the input shaft 5 in an embodiment of the present invention described later
  • the planetary gear corresponds to the first planetary gear 10
  • the ring gear corresponds to the first ring gear 11
  • the first bearing
  • the second bearing corresponds to the fifth and sixth ball bearings B5, B6, and the oil passage is the first oil hole 31, the cavity 30, the annular groove 35 and the second oil hole 36.
  • the one side wall of the eccentric shaft is provided with lubricating oil that has passed through the first bearing in the vicinity of the outer race of the first bearing made of a rolling bearing.
  • a second feature is that an oil guide wall that leads to the entrance of the road is provided continuously.
  • the inlet of the oil passage corresponds to a first oil hole 31 in an embodiment of the present invention described later.
  • the oil guide wall has an arc shape along the outer race of the first bearing, and the oil guide wall is disposed on the rear side in the rotation direction of the transmission shaft.
  • a third feature is that an oil block wall bent radially inward is continuously provided at one end, and an inlet of the oil passage opens between the oil guide wall and the oil block wall.
  • an oil receiving recess facing the oil diffusion member is provided on an inner surface of the gear case above the oil sump chamber.
  • a fourth feature is that a lower portion of the oil receiving recess communicates with the oil sump chamber.
  • an overflow passage through which a predetermined amount or more of lubricating oil accumulated in the oil reservoir chamber flows out to the lower portion of the gear case is connected to the oil reservoir chamber.
  • the oil diffusing member is coupled to the transmission shaft to reduce the rotational unbalance of the eccentric rotating body including the eccentric shaft and the planetary gear.
  • a counterweight to be suppressed, the counterweight extending between the first bearing and the eccentric shaft in a radial direction from the transmission shaft, and the planetary gear and the tip from the tip of the arm portion is that it has a weight portion that has an inner peripheral surface that protrudes between the non-engaging teeth of the ring gear and scoops up the lubricating oil stored in the gear case during rotation.
  • a seventh feature is that the arm portion is provided with a through hole penetrating both side surfaces and continuing to the inner peripheral surface of the weight portion.
  • the lubricating oil diffused in the gear case is received in the oil sump chamber adjacent to the side surface of the first bearing opposite to the eccentric shaft, the influence of centrifugal force is hardly affected.
  • the oil can be stored in the oil sump chamber without being received. Therefore, the first bearing adjacent to the oil sump chamber can be well lubricated by the lubricating oil. Further, when the lubricating oil that has finished the lubrication flows into the oil passage that penetrates between the one side wall and the peripheral wall of the eccentric shaft, the lubricating oil is supplied to the second bearing supported by the peripheral wall under the centrifugal force due to the rotation of the eccentric shaft, It can be lubricated well.
  • the lubricating oil that has passed through the first bearing can be guided to the inlet of the oil passage by the oil guide wall that is connected to the one side wall of the eccentric shaft.
  • the lubrication effect of the second bearing can be enhanced by reducing the leakage of lubricating oil from the bearing.
  • the lubricating oil that has passed through the second bearing and is guided by the oil guide wall can be forced to flow into the oil passage by the oil block wall, and the lubricating oil flowing into the oil passage can be The oil amount can be increased.
  • the lubricating oil shaken off from the oil diffusing member can be captured by the oil receiving recess provided on the inner surface of the gear case and guided to the oil sump chamber. Lubricating oil can be efficiently stored in the reservoir chamber.
  • a predetermined amount or more of the lubricating oil accumulated in the oil sump chamber flows out from the overflow passage to the lower part of the gear case, so that a predetermined amount or more of the lubricating oil necessary for lubricating the first bearing is obtained.
  • the counterweight that suppresses the rotational imbalance of the eccentric rotating body including the eccentric shaft and the planetary gear can be caused to function as the oil diffusing member. Therefore, there is no need to provide a dedicated oil diffusion member, which can contribute to simplification of the structure.
  • a portion of the lubricating oil scooped up by the weight portion of the counterweight is scattered around the arm portion through the through hole of the arm portion, and the weight portion of the weight portion is sandwiched between the arm portion.
  • the first bearing located on the side opposite to the overhang direction can be effectively lubricated.
  • FIG. 1 is a longitudinal front view of a planetary transmission device according to a first embodiment of the invention.
  • FIG. 2 is a sectional view taken along line 2-2 of FIG.
  • FIG. 3 is an explanatory diagram of the operation of the counterweight corresponding to FIG. 2.
  • FIG. 4 is a sectional view taken along line 4-4 of FIG.
  • FIG. 6 is a sectional view taken along line 6-6 of FIG.
  • FIG. 7 is a cross-sectional view taken along line 7-7 in FIG.
  • the perspective view of the coupling body of the input shaft, eccentric shaft, and counterweight which concerns on Example 2 of this invention.
  • Example 1 in which the planetary transmission device of the present invention is applied to a planetary reduction gear will be described.
  • a gear case 1 of a planetary reduction gear R is composed of first and second case halves 1a and 1b which are connected to each other by a plurality of bolts 2 with their open end faces abutted against each other.
  • First and second bearing bosses 3 and 4 are integrally formed on the side walls of the two case halves 1a and 1b, respectively.
  • Each of the first and second bearing bosses 3 and 4 has a cylindrical shape, and both end portions of the first and second bearing bosses 3 and 4 protrude into and out of the side walls of the corresponding first and second case halves 1a and 1b.
  • the first and second bearing bosses 3 and 4 are arranged to be aligned on the main axis X1.
  • the input shaft 5 (transmission shaft 5) is rotatably supported via the first and second ball bearings B1 and B2, and is adjacent to the inner side surface of the first ball bearing B1.
  • a first oil seal S ⁇ b> 1 that is in close contact with the outer peripheral surface of the input shaft 5 is attached to the first bearing boss 3.
  • the output shaft 6 is rotatably supported at both ends of the second bearing boss 4 via third and fourth ball bearings B3 and B4, and adjacent to the inner surface of the fourth ball bearing B4.
  • a second oil seal S2 that is in close contact with the outer peripheral surface of the second bearing boss 4 is mounted.
  • the input shaft 5 and the output shaft 6 are arranged on the main axis X1. That is, the input shaft 5 and the output shaft 6 share the main axis X1.
  • an eccentric shaft 7 is integrally connected to an inner end portion facing the inner side of the gear case 1 from the second ball bearing B 2.
  • the eccentric shaft 7 has its axis, that is, the eccentric axis X 2 is the main axis. It occupies a position offset by a predetermined distance e in the radial direction from X1, and one side wall faces the inner side surface of the second ball bearing B2.
  • the first and second reduction gear trains 8 and 9 are interposed between the input shaft 5 and the output shaft 6.
  • the first reduction gear train 8 (see FIGS. 1 and 2) includes a first planetary gear 10 and a first ring gear 11 that mesh with each other.
  • the first planetary gear 10 is supported on the eccentric shaft 7 through the fifth and sixth ball bearings B5 and B6 arranged at intervals in the axial direction so as to be rotatable and immovable in the axial direction, and the first ring gear 11 is
  • the first and second case halves 1a and 1b are sandwiched and fixed so as to serve as part of the constituent members of the gear case 1, and are centered on the main axis X1.
  • the second reduction gear train 9 (see FIGS. 1 and 4) includes a second planetary gear 13 and a second ring gear 14 that mesh with each other.
  • the second planetary gear 13 is coaxially adjacent to the first planetary gear 10 and is supported on the eccentric shaft 7 through the fifth and sixth ball bearings B5 and B6 together with the first planetary gear 10.
  • the second ring gear 14 is disposed concentrically with the output shaft 6, that is, on the main shaft X ⁇ b> 1 by being fitted and fixed to the outer peripheral surface of the flange 6 a provided integrally with the inner end of the output shaft 6.
  • Both the second planetary gear 13 and the second ring gear 14 have a smaller diameter than the first planetary gear.
  • press fitting, caulking, welding or the like is used for fitting and fixing the second ring gear 14 to the flange 6a.
  • the eccentric shaft 7 revolves around the main axis X1 as the input shaft 5 rotates. Accordingly, the rotation of the input shaft 5 is transmitted to the first planetary gear 10 as a decelerated rotation around the eccentric shaft 7 by rolling the inner periphery of the first planetary gear 10 while meshing with the stationary first ring gear 11.
  • the rotational power input to the input shaft 5 is supplied to the first reduction gear train 8 including the first planetary gear 10 and the first ring gear 11, and the second reduction gear including the second planetary gear 13 and the second ring gear 14. Since the gear train 9 is decelerated in two stages and transmitted to the output shaft 6, a large reduction ratio can be obtained to drive a large load, for example, a vehicle axle (not shown), and a small capacity of the electric motor. And miniaturization are possible.
  • the first and second planetary gears 10 and 13 rotate in the direction opposite to the rotation direction A of the input shaft 5, while the output shaft 6 rotates in the direction opposite to the rotation direction of the first and second planetary gears 10 and 13. As a result, the input shaft 5 and the output shaft 6 are rotated in the same direction A.
  • the second planetary gear 13 integrally has a long axis boss portion 13a supported by the fifth and sixth ball bearings B5 and B6.
  • One end portion of the long axis boss portion 13a protrudes greatly from the rim portion of the second planetary gear 13 to surround the fifth ball bearing B5, and the short axis boss portion 10a of the first planetary gear 10 is formed on the outer periphery of the one end portion.
  • the first and second planetary gears 10 and 13 may be integrally molded. However, the first and second planetary gears 10 and 13 can be integrally formed by combining the individually molded ones as described above. A tooth part can be processed easily.
  • the first planetary gear 10 includes a short shaft boss portion 10a, a web portion 10b extending in a radial direction from the outer periphery of the short shaft boss portion 10a, and a rim portion that is continuous with the outer periphery of the web portion 10b and has teeth formed on the outer periphery. 10c, and at least one end portion of the rim portion 10c opposite to the second planetary gear 13 is a protruding end portion protruding from the side surface of the web portion 10b.
  • FIG. 1 The web portion 10b, the short-axis boss portion 10a, the long-axis boss portion 13a, and the fifth ball bearing B5 are arranged such that their outer surfaces form a single plane.
  • a counterweight 15 is integrally connected to the input shaft 5 between the second ball bearing B ⁇ b> 2 and the first planetary gear 10.
  • the counterweight 15 is arranged such that the phase of the center of gravity G2 around the main axis X1 is shifted from the phase of the eccentric axis X2 by 180 °.
  • the counterweight 15 includes an arm portion 16 that extends in the radial direction from the input shaft 5, and a portion between the front end portion of the arm portion 16 and the teeth portions of the first planetary gear 10 and the first ring gear 11 that are not engaged with each other. It is composed of a weight portion 17 that protrudes.
  • the counterweight 15 has a centrifugal force acting on the center of gravity G1 of the eccentric rotating body composed of the eccentric shaft 7 and the first and second planetary gears 10 and 13, and a centrifugal force acting on the center of gravity G2 of the counterweight 15. Its weight is set to balance the force. As a result, the rotational unbalance amount due to the eccentric rotator can be made zero or significantly reduced.
  • the rotational radius of the center of gravity G2 of the counterweight 15 is made as large as possible.
  • the centrifugal force acting on the center of gravity G2 can be increased, and the weight of the counterweight 15 can be reduced.
  • the displacement s along the main axis X1 between the centers of gravity G1 and G2 is reduced as much as possible.
  • the couple of force exerted on the input shaft 5 by the centrifugal force acting on G2 can be kept small.
  • the arm portion 16 of the counterweight 15 is bent so that the radially outer half portion 16b is offset toward the second ball bearing B2 with respect to the radially inner half portion 16a while making the thickness of each portion uniform. Due to this shape, a first recess 18 connected to the inner peripheral surface of the weight portion 17 is formed on one side surface of the arm portion 16 on the first planetary gear 10 side, and also on the second ball bearing B2 side. On the other side surface, second recesses 19 connected to the base of the arm portion 16 are formed. The first planetary gear 10 is disposed close to the counterweight 15 so that the protruding end portion of the rim portion 10c is accommodated in the first recess 18.
  • the web portion 10b, the short-axis boss portion 10a, the long-axis boss portion 13a, and the outer surface aligned on one plane of the fifth ball bearing B5 have a small gap in the radially inner half 16a of the counterweight 15. Therefore, the housing of the one end portion of the rim portion 10c is not hindered.
  • the counterweight 15 is disposed close to the second ball bearing B2 so that the second recess 19 accommodates the protruding inner end 3a of the first bearing boss 3 that supports the second ball bearing B2.
  • the eccentric shaft 7 approaches the second ball bearing B2 while eliminating a useless space between the second ball bearing B2, the overhang amount of the eccentric shaft 7 from the second ball bearing B2 is increased. Can be reduced as much as possible. Therefore, when a bending load is applied to the eccentric shaft 7 by the meshing reaction forces of the first planetary gear 10 and the first ring gear 11, and the second planetary gear 13 and the second ring gear 14, the load on the second ball bearing B2 is reduced. Thus, the durability can be improved. Further, the reduction of the overhang amount of the eccentric shaft 7 contributes to the reduction of the size of the reduction gear R in the axial direction.
  • the arm portion 16 of the counterweight 15 is bent as described above, so that the thickness of each portion of the arm portion 16 is made equal, and the strength of the arm portion 16 is not reduced.
  • the first and second recesses 18 and 19 can be easily provided.
  • the symbol F indicates a lubricating oil, and a predetermined amount of lubricating oil stored in the bottom of the gear case 1 in the lubricating oil F is indicated by Fa.
  • the counterweight 15 has the following structure of the weight portion 17 so as to function as an oil diffusing member for diffusing the stored lubricating oil Fa when rotating. That is, the weight portion 17 has an arc shape in which the outer peripheral surface is close to the inner peripheral surface of the first ring gear 11, and a concave portion 21 is provided in the circumferential central portion of the inner peripheral surface. Further, on the inner periphery of the weight portion 17, a pair of concave curved surfaces 22 ⁇ / b> A that reach the recess 21 close to the outer peripheral surface of the first planetary gear 10 as it goes from the circumferential ends of the weight portion 17 toward the recess 21. 22B is provided. Further, both end portions in the circumferential direction of the weight portion 17 are formed in a tapered shape by the arc-shaped outer peripheral surface and the pair of concave curved surfaces 22A and 22B.
  • the arm portion 16 of the counterweight 15 is provided with a through hole 23 that penetrates both side surfaces and opens to the bottom of the recess 21.
  • the predetermined amount of the stored lubricating oil Fa at the bottom of the gear case 1 is such that when the leading end of the weight portion 17 in the rotational direction A reaches the lowest position, the leading end sinks into the stored lubricating oil Fa and the first planetary When the gear 10 reaches the uppermost portion, the entire first planetary gear 10 is set to be exposed above the stored lubricating oil Fa.
  • the first bearing boss 3 in the first case half 1 a of the gear case 1 is provided with an annular first oil sump chamber 25.
  • the first oil sump chamber 25 is formed between the second ball bearing B2 and the first oil seal S1 so as to surround the entire circumference of the input shaft 5.
  • an oil receiving recess 26 is provided on the inner surface of the first case half 1a above the first bearing boss 3, and this oil receiving recess 26 is formed on the arm portion 16 when the counterweight 15 reaches the upper position. Arranged to face the outer surface. Further, the oil receiving recess 26 is formed in a fan shape whose width along the rotation direction of the counterweight 15 widens upward. The bottom of the oil receiving recess 26 is connected to the first oil sump chamber 25 via one or a plurality of descending passages 27.
  • the first oil sump chamber 25 is opened to the bottom of the gear case 1 through one or a plurality of first overflow passages 28.
  • the first overflow passage 28 allows excess lubricating oil to be removed from the gear case when the lubricating oil F accumulated in the first oil sump chamber 25 exceeds a predetermined amount sufficient to lubricate the second ball bearing B2 facing the first oil sump chamber 25. It is designed to return to 1.
  • the eccentric shaft 7 is provided with a hollow portion 30 that opens to the end surface thereof. Further, on one side wall of the eccentric shaft 7 facing the second ball bearing B2, the first oil hole 31 communicating between the second ball bearing B2 and the cavity 30 and the lubricating oil that has passed through the second ball bearing B2 are provided. A hook-shaped oil guide wall 32 that leads to the first oil hole 31 is provided.
  • the oil guide wall 32 is formed in an arc shape close to the outer surface of the outer race of the second ball bearing B ⁇ b> 2 so that the inner peripheral surface thereof is continuous with the first oil hole 31.
  • An oil block wall 33 that is bent inward in the radial direction and integrally connected to the outer peripheral surface of the input shaft 5 is connected to the rear end portion in the rotational direction A of the oil guide wall 32.
  • the first oil hole 31 opens between the oil guide wall 32 and the oil block wall 33.
  • the offset amount e of the eccentric shaft 7 with respect to the main axis X is larger than that in the illustrated example, and the first oil hole 31 is formed to have a larger diameter on the axial projection surface so as to overlap a part of the outer race of the second ball bearing B2.
  • the oil guide wall 32 is preferably formed so as to be close to or surround the protruding inner end 3a of the first bearing boss 3 that supports the second ball bearing B2. .
  • the oil guide wall 32 can also be formed in an annular shape. In this case, the oil block wall 33 is unnecessary.
  • annular groove 35 along the inner peripheral surface, and a second groove which communicates with the annular groove 35 to the intermediate portions of the fifth and sixth ball bearings B5 and B6 supported by the peripheral wall.
  • An oil hole 36 is provided.
  • the second oil hole 36 is disposed at a position farthest from the main axis X1 on the peripheral wall of the eccentric shaft 7 or a position near the position. In other words, the second oil hole 36 is arranged in the direction farthest from the main axis X 1 on the peripheral wall of the eccentric shaft 7.
  • a plurality of first and second oil holes 31 and 36 may be provided.
  • the flange 6a of the output shaft 6 that fixes and supports the second ring gear 14 is provided with a plurality of lightening holes 37 that face the third ball bearing B3.
  • the second bearing boss 4 of the gear case 1 is provided with an annular second oil sump chamber 40 that surrounds the output shaft 6 between the third ball bearing B3 and the second oil seal S2.
  • the second oil sump chamber 40 is opened downward in the gear case 1 via the second overflow passage 41.
  • the second overflow passage 41 allows the excess lubricating oil to be removed from the gear case when the lubricating oil F accumulated in the second oil sump chamber 40 exceeds a predetermined amount sufficient to lubricate the third ball bearing B3 facing the second oil sump chamber 40. It is designed to return to 1.
  • the weight portion 17 When the counterweight 15 rotates downward as shown in FIG. 3 while the counterweight 15 is rotating, the weight portion 17 first sinks into the stored lubricating oil Fa at the bottom of the gear case 1 from its leading end, Then, the rotational direction is turned upward while scooping up the lubricating oil by one concave curved surface 22A following the leading end.
  • the one concave curved surface 22A approaches the tooth portion of the first planetary gear 10 in accordance with the direction toward the concave portion 21 in the intermediate portion of the inner peripheral surface of the weight portion 17, so that the one concave curved surface 22A is ugly. Part of the raised lubricating oil is sprinkled on the teeth of the first planetary gear 10.
  • the one concave curved surface 22 ⁇ / b> A is connected to the tooth portion of the first planetary gear 10. While passing each other, the lubricating oil can be effectively sprinkled on the teeth. Therefore, the tooth part of the first planetary gear 10 sufficiently wetted with the lubricating oil meshes with the tooth part of the first ring gear 11, and the meshing part can be effectively lubricated.
  • the weight portion 17 scoops up the stored lubricating oil Fa at the bottom of the gear case 1 by its rotation and diffuses it to the periphery, so that the outer peripheral surface of the weight portion 17 is a smooth arc surface concentric with the rotation center of the counterweight 15.
  • the first planetary gear 10 reaches the top, the entire first planetary gear 10 is exposed above the stored lubricating oil Fa. Therefore, the stirring resistance of the stored lubricating oil Fa by the weight portion 17 and the first planetary gear 10 is small, and power loss can be suppressed to a small value.
  • the second reduction gear train 9 is lubricated with diffusing lubricating oil, so that the amount of immersion of the rotating second ring gear 14 in the stored lubricating oil Fa at the bottom of the gear case 1 is minimized or zero.
  • the stirring resistance of the stored lubricating oil Fa by the teeth of the second ring gear 14 can be reduced or zero.
  • the counterweight 15 also serves as an oil diffusing member for diffusing the stored lubricating oil Fa, a dedicated oil diffusing member is not required, and the structure can be simplified.
  • the weight portion 17 has a pair of concave curved surfaces 22A and 22B on the inner periphery that approach the tooth portion of the first planetary gear 10 and reach the concave portion 21 as it goes from the both end portions to the concave portion 21. Regardless of the rotational direction of 15, the stored lubricating oil Fa at the bottom of the gear case 1 can be scooped up by either one of the concave curved surfaces 22A, 22B, and the same effect as described above can be achieved.
  • the lubricating oil received in the oil receiving recess 26 flows down and accumulates in the first oil sump chamber 25 via the descending passage 27, passes through the bearing while lubricating the second ball bearing B2, and the first oil hole It moves to 31. During this time, the lubricating oil is hardly subjected to rotation from the input shaft 5, and therefore no back flow occurs due to centrifugal force.
  • the lubricating oil that has passed through the second ball bearing B2 is guided by the oil guide wall 32 to the first oil hole 31 connected to the inner peripheral surface thereof, and further flows into the first oil hole 31 by the oil block wall 33. By being forced, it passes through the first oil hole 31 efficiently and flows into the cavity 30 of the eccentric shaft 7.
  • the lubricating oil that has passed through the second ball bearing B2 is efficiently transferred into the annular oil guide wall 32, and is annularly caused by centrifugal force.
  • the oil guide wall 32 flows to the first oil hole 31 connected to the inner peripheral surface of the annular oil guide wall 32 and then to the cavity 30.
  • the lubricating oil flowing into the cavity 30 in this manner is immediately captured in the annular groove 35 and receives a large centrifugal force due to the revolution of the eccentric shaft 7 around the main axis X1 so as to move away from the main axis X1. Flows out from the second oil hole 36 waiting at the farthest position from the main axis X1 or in the vicinity thereof to the fifth and sixth ball bearings B5 and B6, and lubricates these bearings.
  • the lubricating oil that has passed through these bearings becomes splashes to lubricate the first and second reduction gear trains 8 and 9, and the cavity 30 of the eccentric shaft 7
  • the lubricating oil that has flowed out of the opening is also splashed to lubricate the second reduction gear train 9.
  • a predetermined amount or more of the lubricating oil accumulated in the first oil sump chamber 25 flows out from the first overflow passage 28 to the lower part of the gear case 1.
  • a predetermined amount or more of lubricating oil necessary for lubricating the second ball bearing B2 is avoided from being accumulated in the first oil sump chamber 25, so that the operating resistance of the second ball bearing B2 due to the lubricating oil is kept small. Therefore, the circulation of the lubricating oil in the gear case 1 can be improved.
  • the second oil sump chamber 40 a predetermined amount or more of the lubricating oil accumulated in the chamber flows out from the second overflow passage 41 to the lower portion of the gear case 1, thereby exceeding a predetermined amount necessary for the lubrication of the third ball bearing B3. It is possible to prevent the lubricating oil from accumulating. Therefore, the operating resistance of the third ball bearing B3 due to the lubricating oil can be suppressed to a small level, and the lubricating oil can be circulated well in the gear case 1. In addition, since a predetermined amount of lubricating oil can be continuously stored in the second oil reservoir 40, the third ball bearing B3 can be lubricated from the start of the operation of the reduction gear R.
  • the inner peripheral surface of the weight portion 17 of the counterweight 15 is provided with a bowl-shaped concave portion 21 'deepening from both ends toward the center portion.
  • a through hole 23 that penetrates the arm portion 16 opens in the deepest portion of the recess 21 ′.
  • Other configurations are the same as those of the first embodiment, and in the figure, the same reference numerals are given to the corresponding portions with the first embodiment, and the duplicate description is omitted.
  • the weight portion 17 scoops up the stored lubricating oil Fa (see FIG. 3) at the bottom of the gear case 1 by the bowl-shaped concave portion 21, and the lubricating oil flows into the concave portion 21. Outflow to the side of the weight portion 17 as much as possible. As a result, most of the lubricating oil scooped up in the concave portion 21 flows out and diffuses from the through hole 23 of the arm portion 16 toward the inner side surface of the first case half 1a, so that it is directly applied to the second ball bearing B2. Lubrication and supply of lubricating oil to the oil receiving recess 26 can be effectively performed.
  • the weight portion 17 of the counterweight 15 is formed to be bilaterally symmetric when viewed from the axial direction of the input shaft 5, but the center of gravity G2 of the counterweight 15 is opposite to the center of gravity G1 of the eccentric rotor.
  • the phase may be asymmetrical.
  • the concave portion 21 of the weight portion 17 is disposed behind the center portion of the inner peripheral surface of the weight portion 17 in the rotational direction of the weight portion 17, and the concave curved surface 22A is formed to be longer.
  • the scooping distance with respect to the oil Fa can be increased, and the lubricating oil can be sprinkled more effectively on the teeth of the first planetary gear 10.
  • various tooth forms such as a cycloid tooth shape or a circular tooth shape can be adopted for the planetary gear and the ring gear. If the output shaft 6 is changed to an input shaft and the input shaft 5 is changed to an output shaft, the reduction gear R can be changed to a speed increase gear.

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  • General Engineering & Computer Science (AREA)
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  • General Details Of Gearings (AREA)

Abstract

La présente invention concerne un élément de diffusion d'huile (15) qui est couplé à un arbre de transmission (5) supporté par des premiers paliers (B2) dans un carter d'engrenage (1). Un premier réservoir d'huile (25), qui reçoit l'huile de lubrification diffusée par l'élément de diffusion d'huile (15), est disposé sur le carter d'engrenage (1) de façon à être adjacent à la surface latérale des premiers paliers (B2) en regard d'un arbre excentrique (7). L'arbre excentrique (7), qui supporte un satellite (10) par l'intermédiaire de seconds paliers (B5, B6), est pourvu de passages d'huile (30, 31, 36) qui fournissent de l'huile de lubrification, qui a traversé le réservoir d'huile (25) et passe par les premiers paliers (B2), vers les seconds paliers (B5, B6).
PCT/JP2018/002818 2017-02-08 2018-01-30 Structure de lubrification pour dispositif de transmission à trains épicycloïdaux WO2018147120A1 (fr)

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JP2017021725A JP2018128085A (ja) 2017-02-08 2017-02-08 遊星式伝動装置における潤滑構造

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008275094A (ja) * 2007-05-01 2008-11-13 Ntn Corp インホイールモータ駆動装置
JP2010203588A (ja) * 2009-03-05 2010-09-16 Toyota Motor Corp 遊星歯車機構の潤滑構造
JP2016114184A (ja) * 2014-12-16 2016-06-23 Ntn株式会社 サイクロイド減速機およびこれを備えたインホイールモータ駆動装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008275094A (ja) * 2007-05-01 2008-11-13 Ntn Corp インホイールモータ駆動装置
JP2010203588A (ja) * 2009-03-05 2010-09-16 Toyota Motor Corp 遊星歯車機構の潤滑構造
JP2016114184A (ja) * 2014-12-16 2016-06-23 Ntn株式会社 サイクロイド減速機およびこれを備えたインホイールモータ駆動装置

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