WO2018147120A1 - Lubrication structure for planetary transmission device - Google Patents

Lubrication structure for planetary transmission device 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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French (fr)
Japanese (ja)
Inventor
亮輔 淺井
圭宏 吉田
Original Assignee
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/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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.

Abstract

In the present invention, an oil diffusion member (15) is coupled to a transmission shaft (5) supported by first bearings (B2) in a gear case (1). A first oil reservoir (25), which receives lubricating oil diffused by the oil diffusion member (15), is provided to the gear case (1) so as to be adjacent to the side surface of the first bearings (B2) opposite to an eccentric shaft (7). The eccentric shaft (7), which supports a planetary gear (10) via second bearings (B5, B6), is provided with oil passages (30, 31, 36) that supply lubricating oil, which has passed from the oil reservoir (25) and through the first bearings (B2), to the second bearings (B5, B6).

Description

遊星式伝動装置における潤滑構造Lubrication structure in planetary transmission
　本発明は，減速機や増速機に用いられる遊星式伝動装置における潤滑構造に関する。 The present invention relates to a lubricating structure in a planetary transmission device used for a reduction gear or a speed increaser.
　従来，遊星式伝動装置として，下記特許文献１に開示されるように，ギヤケースと，該ギヤケースの両側壁にそれぞれ回転自在に支持される第１伝動軸及び第２伝動軸と，第１伝動軸に結合され，該第１伝動軸の回転に伴ない第１伝動軸の軸線周りに偏心回転する偏心軸と，該偏心軸に回転自在に支持される遊星ギヤと，ギヤケースに第１伝動軸と同軸状に固定されて遊星ギヤと噛合するリングギヤと，遊星ギヤの遊星運動を回転運動に変換して第２伝動軸に伝達する運動変換機構とを備えるものが知られている。そして，このような遊星式伝動装置においては，第２伝動軸に取り付けられる油拡散部材の回転により，ギヤケース内に貯留する潤滑油を周囲に拡散させ，その拡散させた潤滑油を，第２伝動軸に設けた導油路で受けて被潤滑部に供給するようにした潤滑構造が採用されている。 Conventionally, 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. In such a planetary transmission, 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.
特許第４９７５２７４号公報Japanese Patent No. 4975274
　しかしながら，上記のような潤滑構造では，ギヤケース内の拡散潤滑油を第２伝動軸の導油路で捉えたとしても，その導油路は，第２伝動軸の回転中心方向に向かうように形成されているため，導油路で捉えられた潤滑油は，第２伝動軸の回転に伴なう遠心力に抗して流れなければならない。したがって潤滑油は被潤滑部まで到達しにくく，所望の潤滑を達成することが困難である。 However, in the lubricating structure as described above, even if the diffusion lubricating oil in the gear case is caught by the oil transmission path of the second transmission shaft, 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.
　本発明は，かかる事情に鑑みてなされたもので，油拡散部材によりギヤケース内に拡散させた潤滑油を有効に利用して被潤滑部を効果的に潤滑し得るようにした，遊星式伝動装置における潤滑構造を提供することを目的とする。 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.
　上記目的を達成するために，本発明では，ギヤケースと，該ギヤケースに第１ベアリングを介して回転自在に支持される伝動軸と，該伝動軸に一体的に結合される偏心軸と，該偏心軸の周壁に第２ベアリングを介して支持される遊星ギヤと，前記ギヤケースに前記伝動軸と同軸状に固定されるリングギヤとを備え，前記偏心軸の一側壁が前記第１ベアリングに対面している遊星式伝動装置における潤滑構造であって，前記ギヤケースの底部に貯留される潤滑油と，前記潤滑油を前記ギヤケース内に拡散させる油拡散部材と，前記第１ベアリングの，前記偏心軸と反対側の側面に隣接するよう前記ギヤケースに設けられ，拡散した前記潤滑油を受容する油溜め室と，前記偏心軸に，前記一側壁及び前記周壁間を貫通するように設けられ，前記油溜め室から前記第１ベアリングを通過した潤滑油を前記第２ベアリングに供給する油路とを備えることを第１の特徴とする。 In order to achieve the above object, according to the present invention, 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.
　尚，前記伝動軸は，後述する本発明の実施例中の入力軸５に対応し，前記遊星ギヤは第１遊星ギヤ１０に対応し，リングギヤは第１リングギヤ１１に対応し，第１ベアリングは第２ボールベアリングＢ２に対応し，第２ベアリングは第５及び第６ボールベアリングＢ５，Ｂ６に対応し，前記油路は第１油孔３１，空洞部３０，環状溝３５及び第２油孔３６に対応する。 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, and the first bearing Corresponding to the second ball bearing B2, 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. Corresponding to
　また本発明では，第１の特徴に加えて，前記偏心軸の前記一側壁には，転がり軸受よりなる前記第１ベアリングのアウタレースに近接して，該第１ベアリングを通過した潤滑油を前記油路の入口に誘導する油ガイド壁が連設されることを第２の特徴とする。 According to the present invention, in addition to the first feature, 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.
　尚，前記油路の入口は，後述する本発明の実施例中の第１油孔３１に対応する。 The inlet of the oil passage corresponds to a first oil hole 31 in an embodiment of the present invention described later.
　さらに本発明では，第２の特徴に加えて，前記油ガイド壁は，前記第１ベアリングのアウタレースに沿うように円弧状をなすと共に，該油ガイド壁の，前記伝動軸の回転方向後方側の一端に半径方向内方へ屈曲した油ブロック壁が連設され，これら油ガイド壁及び油ブロック壁間に前記油路の入口が開口することを第３の特徴とする。 Further, in the present invention, in addition to the second feature, 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.
　さらにまた本発明では，第１～第３の特徴の何れかに加えて，前記ギヤケースの，前記油溜め室より上方の内側面に，前記油拡散部材に対面する油受け凹部が設けられ，該油受け凹部の下部が前記油溜め室に連通することを第４の特徴とする。 Furthermore, in the present invention, in addition to any of the first to third features, 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.
　さらにまた本発明では，第１～第４の特徴の何れかに加えて，前記油溜め室に溜まる所定量以上の潤滑油を前記ギヤケースの下部に流出させるオーバフロー通路が該油溜め室に接続されることを第５の特徴とする。 Furthermore, according to the present invention, in addition to any of the first to fourth features, 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. This is the fifth feature.
　さらにまた本発明では，第１～第５の特徴の何れかに加えて，前記油拡散部材が，前記伝動軸に結合されて，前記偏心軸及び遊星ギヤを含む偏心回転体の回転アンバランスを抑制するカウンタウエイトであり，該カウンタウエイトは，前記第１ベアリングと前記偏心軸との間で前記伝動軸から半径方向に延出するアーム部と，該アーム部の先端部から前記遊星ギヤ及び前記リングギヤの噛合しない歯部間に張り出し，回転時，前記ギヤケースに貯留する前記潤滑油を掬い上げる内周面を持つウエイト部とを有することを第６の特徴とする。 Furthermore, in the present invention, in addition to any of the first to fifth features, 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 A sixth feature 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.
　さらにまた本発明では，第６の特徴に加えて，前記アーム部には，その両側面を貫通して前記ウエイト部の内周面に連なる透孔が設けられることを第７の特徴とする。 Furthermore, in the present invention, in addition to the sixth feature, 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.
　本発明の第１の特徴によれば，ギヤケース内に拡散した潤滑油は，第１ベアリングの，偏心軸と反対側の側面に隣接する油溜め室に受容されるので，遠心力の影響を殆ど受けることなく該油溜め室に溜まることができる。したがって，その潤滑油により，該油溜め室に隣接する第１ベアリングを良好に潤滑することができる。またその潤滑を終えた潤滑油は，偏心軸の一側壁及び周壁間を貫通する油路に流入すると，偏心軸の回転による遠心力を受けて上記周壁に支持される第２ベアリングに供給され，それを良好に潤滑することができる。 According to the first feature of the present invention, since 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.
　本発明の第２の特徴によれば，第１ベアリングを通過した潤滑油を，偏心軸の前記一側壁に連設される油ガイド壁により前記油路の入口に誘導することができ，第１ベアリングからの潤滑油の漏れを少なくして，第２ベアリングの潤滑効果を高めることができる。 According to the second feature of the present invention, 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.
　本発明の第３特徴によれば，第２ベアリングを通過して油ガイド壁により誘導された潤滑油を油ブロック壁により強制的に前記油路に流入させることができ，油路に流入する潤滑油量の増加を図ることができる。 According to the third aspect of the present invention, 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.
　本発明の第４の特徴によれば，油拡散部材より振り切られた潤滑油を，ギヤケースの内側面に設けた油受け凹部で捕捉して前記油溜め室に誘導することができて，前記油溜め室には潤滑油を効率よく溜めることができる。 According to the fourth feature of the present invention, 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.
　本発明の第５の特徴によれば，油溜め室に溜まる所定量以上の潤滑油をオーバフロー通路よりギヤケースの下部に流出させることで，第１ベアリングの潤滑に必要な所定量以上の潤滑油が油溜め室に溜まることを回避して，第１ベアリングの潤滑油による作動抵抗を小さく抑えると共に，ギヤケース内での潤滑油の循環を良好にすることができる。 According to the fifth aspect of the present invention, 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. By avoiding accumulation in the oil sump chamber, it is possible to reduce the operating resistance of the first bearing due to the lubricating oil, and to improve the circulation of the lubricating oil in the gear case.
　本発明の第６の特徴によれば，偏心軸及び遊星ギヤを含む偏心回転体の回転アンバランスを抑制するカウンタウエイトを油拡散部材として機能させることができる。したがって，専用の油拡散部材を設ける必要がなく，構造の簡素化に寄与し得る。 According to the sixth aspect of the present invention, 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.
　本発明の第７の特徴によれば，カウンタウエイトのウエイト部により掬い上げられた潤滑油の一部がアーム部の透孔を通過して周囲に飛散して，アーム部を挟んでウエイト部の張り出し方向と反対側に位置する第１ベアリングを効果的に潤滑することができる。 According to the seventh feature of the present invention, 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.
本発明の実施例１に係る遊星式伝動装置の縦断正面図。BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a longitudinal front view of a planetary transmission device according to a first embodiment of the invention. 図１の２－２線断面図。FIG. 2 is a sectional view taken along line 2-2 of FIG. 図２に対応する，カウンタウエイトの作用説明図。FIG. 3 is an explanatory diagram of the operation of the counterweight corresponding to FIG. 2. 図１の４－４線断面図。FIG. 4 is a sectional view taken along line 4-4 of FIG. 入力軸，偏心軸及びカウンタウエイトの結合体の斜視図。The perspective view of the coupling body of an input shaft, an eccentric shaft, and a counterweight. 図１の６－６線断面図。FIG. 6 is a sectional view taken along line 6-6 of FIG. 図１の７－７線断面図。FIG. 7 is a cross-sectional view taken along line 7-7 in FIG. 本発明の実施例２に係る入力軸，偏心軸及びカウンタウエイトの結合体の斜視図。The perspective view of the coupling body of the input shaft, eccentric shaft, and counterweight which concerns on Example 2 of this invention.
　本発明の実施形態を添付図面に基づいて以下に説明する。 Embodiments of the present invention will be described below with reference to the accompanying drawings.
　本発明の遊星式伝動装置を遊星式減速機に適用した実施例１について説明する。 Example 1 in which the planetary transmission device of the present invention is applied to a planetary reduction gear will be described.
　先ず，この遊星式減速機における伝動系の説明より始める。 First, let's start with an explanation of the transmission system in this planetary reducer.
　図１において，遊星式減速機Ｒのギヤケース１は，互いに開放端面を突き合わせて複数本のボルト２により結合される第１及び第２ケース半体１ａ，１ｂよりなっており，これら第１及び第２ケース半体１ａ，１ｂの側壁には第１及び第２軸受ボス３，４がそれぞれ一体に形成される。これら第１及び第２軸受ボス３，４は，それぞれ円筒状をなしていて，その両端部を対応する第１及び第２ケース半体１ａ，１ｂの側壁の内外に突出させている。これら第１及び第２軸受ボス３，４は，主軸線Ｘ１上に並ぶように配置される。 In FIG. 1, 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.
　第１軸受ボス３の両端部において入力軸５（伝動軸５）が第１及び第２ボールベアリングＢ１，Ｂ２を介して回転自在に支持されると共に，第１ボールベアリングＢ１の内側面に隣接して入力軸５の外周面に密接する第１オイルシールＳ１が第１軸受ボス３に装着される。また第２軸受ボス４の両端部において出力軸６が第３及び第４ボールベアリングＢ３，Ｂ４を介して回転自在に支持されると共に，第４ボールベアリングＢ４の内側面に隣接して出力軸６の外周面に密接する第２オイルシールＳ２が第２軸受ボス４に装着される。こうして，入力軸５及び出力軸６は主軸線Ｘ１上に配置される。即ち，入力軸５及び出力軸６は主軸線Ｘ１を中心に共有する。 At both ends of the first bearing boss 3, 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. Thus, 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.
　入力軸５において，第２ボールベアリングＢ２よりギヤケース１内方に臨む内端部には偏心軸７が一体に連設されており，この偏心軸７は，その軸線，即ち偏心軸線Ｘ２が主軸線Ｘ１より半径方向に所定距離ｅオフセットした位置を占め，そして一側壁が第２ボールベアリングＢ２の内側面に対向している。 In the input shaft 5, 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.
　入力軸５及び出力軸６間には，第１及び第２減速ギヤ列８，９が介装される。その第１減速ギヤ列８（図１及び図２参照）は，互いに噛合する第１遊星ギヤ１０及び第１リングギヤ１１より構成される。第１遊星ギヤ１０は，偏心軸７に，軸方向に間隔を空けて並ぶ第５及び第６ボールベアリングＢ５，Ｂ６を介して回転自在且つ軸方向移動不能に支持され，また第１リングギヤ１１は，ギヤケース１の構成部材の一部を兼ねるように，第１及び第２ケース半体１ａ，１ｂ間に挟持固定されて，主軸線Ｘ１上に中心を置いている。 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.
　また第２減速ギヤ列９（図１及び図４参照）は，互いに噛合する第２遊星ギヤ１３及び第２リングギヤ１４より構成される。その第２遊星ギヤ１３は，第１遊星ギヤ１０に同軸状に隣接して結合され，第１遊星ギヤ１０と共に第５及び第６ボールベアリングＢ５，Ｂ６を介して偏心軸７に支持される。また第２リングギヤ１４は，出力軸６がその内端に一体に備えるフランジ６ａ外周面に嵌合，固着されて，出力軸６と同心状に，即ち主軸Ｘ１上に配置される。これら第２遊星ギヤ１３及び第２リングギヤ１４は，いずれも第１遊星ギヤより小径である。フランジ６ａへの第２リングギヤ１４の嵌合，固着には，圧入，かしめ，溶接等が用いられる。 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. Further, 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. For fitting and fixing the second ring gear 14 to the flange 6a, press fitting, caulking, welding or the like is used.
　この伝動系の作用について説明する。 The operation of this transmission system will be explained.
　例えば，図示しない電動モータから入力軸５に回転動力が入力されると，この入力軸５の回転に伴ない偏心軸７は主軸線Ｘ１周りに公転する。これに伴い第１遊星ギヤ１０が不動の第１リングギヤ１１と噛み合いながらその内周を転がることにより，入力軸５の回転が第１遊星ギヤ１０に偏心軸７周りの減速した自転として伝達する。このときの入力軸５及び第１遊星ギヤ１０間の減速比λ１は次式で表すことができる。
　　　　　　　λ１＝Ｚ１／（Ｚ１－Ｚ２） For example, when rotational power is input to the input shaft 5 from an electric motor (not shown), 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 reduction ratio λ1 between the input shaft 5 and the first planetary gear 10 at this time can be expressed by the following equation.
λ1 = Z1 / (Z1-Z2)
　但し，Ｚ１・・・第１遊星ギヤ１０の歯数
　　　　Ｚ２・・・第１リングギヤ１１の歯数
　　　　Ｚ１＜Ｚ２ However, Z1... Number of teeth of first planetary gear 10 Z2... Number of teeth of first ring gear 11 Z1 <Z2
　第１遊星ギヤ１０が自転すると，この第１遊星ギヤ１０と一体化した第２遊星ギヤ１３も同時に偏心軸７周りに自転することにより，第２リングギヤ１４を介して出力軸６が減速駆動される。このときの第２遊星ギヤ１３及び第２リングギヤ１４間の減速比λ２は次式で表すことができる。
　　　　　　　λ２＝Ｚ４（Ｚ１－Ｚ２）／（Ｚ１×Ｚ４－Ｚ２×Ｚ３) When the first planetary gear 10 rotates, the second planetary gear 13 integrated with the first planetary gear 10 also rotates around the eccentric shaft 7 at the same time, so that the output shaft 6 is driven to decelerate via the second ring gear 14. The The reduction ratio λ2 between the second planetary gear 13 and the second ring gear 14 at this time can be expressed by the following equation.
λ2 = Z4 (Z1−Z2) / (Z1 × Z4−Z2 × Z3)
　但し，Ｚ３・・・第２遊星ギヤ１３の歯数
　　　　Ｚ４・・・第２リングギヤ１４の歯数
　　　　Ｚ３＜Ｚ４ However, Z3: Number of teeth of the second planetary gear 13 Z4: Number of teeth of the second ring gear 14 Z3 <Z4
　したがって，入力軸５及び出力軸６間の総合減速比λは次式で表すことができる。
　　　　　　　λ＝λ１×λ２＝Ｚ１×Ｚ４／（Ｚ１×Ｚ４－Ｚ２×Ｚ３） Therefore, the overall reduction ratio λ between the input shaft 5 and the output shaft 6 can be expressed by the following equation.
λ = λ1 × λ2 = Z1 × Z4 / (Z1 × Z4-Z2 × Z3)
　このように，入力軸５に入力された回転動力は，第１遊星ギヤ１０及び第１リングギヤ１１よりなる第１減速ギヤ列８と，第２遊星ギヤ１３及び第２リングギヤ１４よりなる第２減速ギヤ列９とにより２段階減速されて出力軸６に伝達されるので，大なる減速比を得て，大なる負荷，例えば図示しない車両の車軸を駆動することができると共に，電動モータの小容量化，小型化が可能となる。 As described above, 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.
　この伝動中，第１遊星ギヤ１０の主軸線Ｘ１周りの公転及び偏心軸線Ｘ２周りの自転，即ち遊星運動は，第２減速ギヤ列９により単純な回転運動に変換されて，出力軸６に伝達されるので，出力軸６に歳差運動は生じない。 During this transmission, the revolution of the first planetary gear 10 around the main axis X 1 and the rotation around the eccentric axis X 2, that is, the planetary movement, is converted into a simple rotational movement by the second reduction gear train 9 and transmitted to the output shaft 6. Therefore, no precession occurs on the output shaft 6.
　また第１及び第２遊星ギヤ１０，１３は，入力軸５の回転方向Ａと逆方向に自転する一方，出力軸６は，第１及び第２遊星ギヤ１０，１３の自転方向と逆方向に回転するので，結局，入力軸５及び出力軸６の回転方向は同方向Ａとなる。 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.
　ここで，第１及び第２遊星ギヤ１０，１３について詳しく説明する。 Here, the first and second planetary gears 10 and 13 will be described in detail.
　第２遊星ギヤ１３は，第５及び第６ボールベアリングＢ５，Ｂ６に支持される長軸ボス部１３ａを一体に有する。この長軸ボス部１３ａ一端部は，第２遊星ギヤ１３のリム部から大きく張り出して第５ボールベアリングＢ５を囲繞しており，その一端部の外周に第１遊星ギヤ１０の短軸ボス部１０ａが嵌合，固着される。その固着には，圧入，カシメ，溶接等が用いられる。 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. Are fitted and fixed. For the fixing, press fitting, caulking, welding or the like is used.
　第１及び第２遊星ギヤ１０，１３は一体成形してもよいが，上記のように個別成形したものを一体に結合することにより，第１及び第２遊星ギヤ１０，１３の単体時にそれぞれの歯部を容易に加工することができる。 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.
　第１遊星ギヤ１０は，短軸ボス部１０ａと，この短軸ボス部１０ａの外周より半径方向に広がるウェブ部１０ｂと，このウェブ部１０ｂの外周に連なり，外周に歯部を形成したリム部１０ｃとより構成され，そのリム部１０ｃの，少なくとも第２遊星ギヤ１３と反対側の一端部は，上記ウェブ部１０ｂの側面より突出する突出端部となっている。これにより，第１遊星ギヤ１０のリム部１０ｃの幅，即ち歯幅を，この第１遊星ギヤ１０に隣接する第２リングギヤ１４に干渉されることなく，充分に確保することができる。上記ウェブ部１０ｂ，短軸ボス部１０ａ，長軸ボス部１３ａ及び第５ボールベアリングＢ５は，これらの外側面が一平面を形成するように配置される。 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. Thereby, the width | variety of the rim | limb part 10c of the 1st planetary gear 10, ie, a tooth | gear width, can fully be ensured, without interfering with the 2nd ring gear 14 adjacent to this 1st planetary gear 10. FIG. 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.
　図１，図２及び図３において，入力軸５には，第２ボールベアリングＢ２及び第１遊星ギヤ１０間においてカウンタウエイト１５が一体に連設される。このカウンタウエイト１５は，その重心Ｇ２の主軸線Ｘ１周りの位相が偏心軸線Ｘ２の位相と１８０°ずれるように配置される。 1, 2 and 3, 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 °.
　このカウンタウエイト１５は，入力軸５から半径方向に延出するアーム部１６と，このアーム部１６の先端部から第１遊星ギヤ１０及び第１リングギヤ１１の噛み合っていない歯部相互間に向かって張り出すウエイト部１７とよりなっている。このカウンタウエイト１５は，入力軸５の回転時，偏心軸７及び第１，第２遊星ギヤ１０，１３よりなる偏心回転体の重心Ｇ１に働く遠心力と，カウンタウエイト１５の重心Ｇ２に働く遠心力とが釣り合うように，その重量が設定される。これにより，偏心回転体による回転アンバランス量をゼロにし，もしくは著しく減少させることができる。 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. When the input shaft 5 is rotated, 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.
　またカウンタウエイト１５のウエイト部１７を第１，第２遊星ギヤ１０，１３の噛み合わない歯部間のスペースを利用して配置したことにより，カウンタウエイト１５の重心Ｇ２の回転半径を極力大きくして，重心Ｇ２に働く遠心力を増加させ，カウンタウエイト１５の軽量化を図ることができ，これと同時に，重心Ｇ１，Ｇ２間の主軸線Ｘ１に沿うずれｓを極力小さくして，両重心Ｇ１，Ｇ２に働く遠心力が入力軸５に及ぼす偶力を小さく抑えることができる。 Further, by arranging the weight portion 17 of the counterweight 15 using the space between the tooth portions where the first and second planetary gears 10 and 13 are not meshed with each other, 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. At the same time, 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.
　このカウンタウエイト１５のアーム部１６は，各部の肉厚を均等にしながら半径方向内方半部１６ａに対して半径方向外方半部１６ｂが第２ボールベアリングＢ２側にオフセットするように屈曲した形状をなしており，この形状により，アーム部１６の，第１遊星ギヤ１０側の一側面には，ウエイト部１７の内周面に連なる第１凹所１８が，また第２ボールベアリングＢ２側の他側面には，アーム部１６の根元に連なる第２凹所１９がそれぞれ形成される。そして，第１遊星ギヤ１０は，そのリム部１０ｃの突出端部が上記第１凹所１８に収容されるよう，カウンタウエイト１５に近接配置される。 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.
　このとき，ウェブ部１０ｂ，短軸ボス部１０ａ，長軸ボス部１３ａ及び第５ボールベアリングＢ５の一平面上に並ぶ外側面は，カウンタウエイト１５の半径方向内方半部１６ａに小間隙を存して対面し，リム部１０ｃの一端部の第１凹所１８への収容を妨げない。 At this time, 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.
　更に，カウンタウエイト１５は，第２凹所１９が第２ボールベアリングＢ２を支持する第１軸受ボス３の突出した内端部３ａを収容するよう，第２ボールベアリングＢ２に近接配置される。 Further, 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.
　かくして，偏心軸７は，第２ボールベアリングＢ２との間の無駄なスペースを排除して，第２ボールベアリングＢ２に近づくことになるので，偏心軸７の，第２ボールベアリングＢ２からのオーバハング量を極力減少させることができる。したがって，第１遊星ギヤ１０と第１リングギヤ１１，第２遊星ギヤ１３と第２リングギヤ１４の各噛合反力により偏心軸７に曲げ荷重が作用したとき，第２ボールベアリングＢ２の荷重負担を少なくして，その耐久性の向上を図ることができる。また偏心軸７のオーバハング量の減少は，減速機Ｒの軸方向のコンパクト化に資することにもなる。 Thus, since 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.
　またカウンタウエイト１５のアーム部１６は，上述のように屈曲した形状をなすことにより，アーム部１６各部の肉厚を等しくしてアーム部１６の強度を低下させずに，アーム部１６の両側面に第１及び第２凹所１８，１９を簡単に設けることができる。 Further, 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.
　次に，この遊星式減速機Ｒにおける潤滑系について説明する。 Next, the lubrication system in the planetary reduction gear R will be described.
　図１～図４において，符号Ｆは潤滑油を示し，その潤滑油Ｆにおいて特にギヤケース１の底部に貯留される所定量の潤滑油をＦａで示す。 1 to 4, 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.
　カウンタウエイト１５は，その回転時，上記貯留潤滑油Ｆａを拡散させる油拡散部材として機能すべく，そのウエイト部１７が次のような構造になっている。即ち，ウエイト部１７は，その外周面が第１リングギヤ１１の内周面に近接した円弧状をなし，またその内周面の周方向中央部には凹部２１が設けられる。さらにウエイト部１７の内周には，ウエイト部１７の周方向両端部から上記凹部２１に向かうに応じて第１遊星ギヤ１０の外周面に近接して上記凹部２１に達する一対の凹曲面２２Ａ，２２Ｂが設けられる。またウエイト部１７の周方向両端部は，上記円弧状の外周面と一対の凹曲面２２Ａ，２２Ｂとにより先細り状に形成される。 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.
　一方，カウンタウエイト１５のアーム部１６には，その両側面を貫通して上記凹部２１の底部に開口する透孔２３が設けられる。 On the other hand, 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.
　ギヤケース１底部の貯留潤滑油Ｆａの所定量は，ウエイト部１７の回転方向Ａに向かう先頭端部が最下部に達したとき，その先頭端部が貯留潤滑油Ｆａ中に沈み，且つ第１遊星ギヤ１０が最上部に達したとき，その第１遊星ギヤ１０全体が貯留潤滑油Ｆａの上方に露出するように設定される。 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.
　さらに潤滑系の説明は続く。図１，図６及び図７において，ギヤケース１の第１ケース半体１ａにおける第１軸受ボス３には環状の第１油溜め室２５が設けられる。この第１油溜め室２５は，第２ボールベアリングＢ２及び第１オイルシールＳ１間に挟まれ，且つ入力軸５の全周を囲むように形成される。 Further explanation of the lubrication system will continue. 1, 6 and 7, 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.
　また第１軸受ボス３より上方の第１ケース半体１ａの内側面には油受け凹部２６が設けられ，この油受け凹部２６は，カウンタウエイト１５が上方位置に到来したとき，アーム部１６の外側面と対面するように配置される。またこの油受け凹部２６は，カウンタウエイト１５の回転方向に沿う幅が上方に向かって広がる扇形に形成される。そしてこの油受け凹部２６の底部は，１本又は複数本の下降通路２７を介して第１油溜め室２５に接続される。 Further, 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.
　また第１油溜め室２５は，１本又は複数本の第１オーバフロー通路２８を介してギヤケース１の底部に開放される。この第１オーバフロー通路２８は，第１油溜め室２５に溜まる潤滑油Ｆが，第１油溜め室２５に臨む第２ボールベアリングＢ２の潤滑に足る所定量以上となると，余剰の潤滑油をギヤケース１内に戻すようになっている。 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.
　図１，図６及び図７において，偏心軸７には，その端面に開放する空洞部３０が設けられる。また偏心軸７の，第２ボールベアリングＢ２に対向する一側壁には，第２ボールベアリングＢ２及び空洞部３０間を連通する第１油孔３１と，第２ボールベアリングＢ２を通過した潤滑油を第１油孔３１に誘導する庇状の油ガイド壁３２とが設けられる。この油ガイド壁３２は，第２ボールベアリングＢ２のアウタレースの外側面に近接した円弧状をなして，その内周面が第１油孔３１に連なるように形成される。この油ガイド壁３２の回転方向Ａ後方端部には，半径方向内方に屈曲して入力軸５の外周面に一体に接続される油ブロック壁３３が連設される。そして第１油孔３１は，上記油ガイド壁３２及び油ブロック壁３３間に開口する。 1, 6, and 7, 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.
　尚，偏心軸７の主軸線Ｘに対するオフセット量ｅが図示例より大きく，軸方向投影面上で第１油孔３１が第２ボールベアリングＢ２のアウタレースの一部と重なる程，大径に形成される場合には，油ガイド壁３２は，第２ボールベアリングＢ２を支持する第１軸受ボス３の突出した内端部３ａに近接するように，もしくはそれを囲繞するように形成されることが望ましい。 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. In this case, 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. .
　また油ガイド壁３２は環状に形成することもできる。この場合，油ブロック壁３３は不要となる。 The oil guide wall 32 can also be formed in an annular shape. In this case, the oil block wall 33 is unnecessary.
　さらに偏心軸７の周壁には，その内周面に沿う環状溝３５と，この環状溝３５を，上記周壁に支持される第５及び第６ボールベアリングＢ５，Ｂ６の中間部に連通させる第２油孔３６とが設けられる。この第２油孔３６は，偏心軸７の周壁における主軸線Ｘ１からの最遠位置もしくはその近傍位置に配置される。即ち，第２油孔３６は，偏心軸７の周壁において主軸線Ｘ１から最も離れる方向に偏って配置される。尚，第１及び第２油孔３１，３６の個数は複数でもよい。 Further, on the peripheral wall of the eccentric shaft 7, there is an 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.
　次に図１及び図４において，出力軸６の，第２リングギヤ１４を固定支持するフランジ６ａには，第３ボールベアリングＢ３に対向する複数の肉抜き孔３７が設けられる。またギヤケース１の第２軸受ボス４には，第３ボールベアリングＢ３及び第２オイルシールＳ２間において出力軸６を囲繞する環状の第２油溜め室４０が設けられる。この第２油溜め室４０は，第２オーバフロー通路４１を介してギヤケース１内の下方へ開放される。この第２オーバフロー通路４１は，第２油溜め室４０に溜まる潤滑油Ｆが，第２油溜め室４０に臨む第３ボールベアリングＢ３の潤滑に足る所定量以上となると，余剰の潤滑油をギヤケース１内に戻すようになっている。 1 and 4, 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.
　この潤滑系の作用について説明する。 The operation of this lubrication system will be explained.
　カウンタウエイト１５の回転中，図３に示すようにカウンタウエイト１５が下向きに回転していくと，そのウエイト部１７は，先ず，その先頭端部からギヤケース１底部の貯留潤滑油Ｆａに沈み込み，そして先頭端部に続く一方の凹曲面２２Ａによりその潤滑油を掬い上げながら，回転方向を上向きに転じていく。ところで，上記一方の凹曲面２２Ａは，ウエイト部１７の内周面中間部の凹部２１に向うに応じて第１遊星ギヤ１０の歯部に接近していくので，上記一方の凹曲面２２Ａにより掬い上げられた潤滑油の一部は第１遊星ギヤ１０の歯部に振りかけられる。特に，入力軸５と一体回転するカウンタウエイト１５の回転方向Ａと第１遊星ギヤ１０の回転方向とは逆であることから，上記一方の凹曲面２２Ａは，第１遊星ギヤ１０の歯部とすれ違いながら，その歯部に潤滑油を効果的に振りかけることができる。したがって潤滑油で充分に濡れた第１遊星ギヤ１０の歯部が第１リングギヤ１１の歯部と噛合することになり，その噛合部を効果的に潤滑することができる。 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. By the way, 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. In particular, since the rotation direction A of the counterweight 15 that rotates integrally with the input shaft 5 is opposite to the rotation direction 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.
　また上記一方の凹曲面２２Ａにより掬い上げられた潤滑油の他の一部は，ウエイト部１７の内周面中間部の凹部２１へと誘導され，その潤滑油は，カウンタウエイト１５の回転に伴ない凹部２１により振り回されることにより，ギヤケース１内の広範囲に拡散し，飛沫となってギヤケース１内の各部を潤滑する。またウエイト部１７の内周面側方から流出した潤滑油は，特に第２リングギヤ１４の歯部に振りかかり，第２減速ギヤ列９の噛合部を潤滑する。 Further, another part of the lubricating oil scooped up by the one concave curved surface 22A is guided to the concave portion 21 in the middle portion of the inner peripheral surface of the weight portion 17, and the lubricating oil is accompanied by the rotation of the counterweight 15. By being swung around by the recesses 21 that are not present, they diffuse in a wide range in the gear case 1 and become splashes to lubricate each part in the gear case 1. Further, the lubricating oil that has flowed out from the side of the inner peripheral surface of the weight portion 17 is sprinkled particularly on the teeth of the second ring gear 14 and lubricates the meshing portion of the second reduction gear train 9.
　このように，ウエイト部１７は，その回転によりギヤケース１底部の貯留潤滑油Ｆａを掬い上げて周囲に拡散させるので，ウエイト部１７の外周面がカウンタウエイト１５の回転中心と同心の滑らかな円弧面をなすことと相俟って，上記貯留潤滑油Ｆａの攪拌が少ない上，第１遊星ギヤ１０が最上部に達したときは，第１遊星ギヤ１０全体が上記貯留潤滑油Ｆａの上方に露出するので，ウエイト部１７及び第１遊星ギヤ１０による上記貯留潤滑油Ｆａの攪拌抵抗が小さく，動力損失を小さく抑えることができる。 In this way, 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. When 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.
　また第２減速ギヤ列９の潤滑を，拡散する潤滑油で行うことにより，回転する第２リングギヤ１４の，ギヤケース１底部の貯留潤滑油Ｆａへの浸漬量を極力少なくし，もしくはゼロとすることが可能となり，第２リングギヤ１４の歯部による貯留潤滑油Ｆａの攪拌抵抗を少なくし，もしくはゼロとすることができる。 Further, 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.
　またカウンタウエイト１５が貯留潤滑油Ｆａを拡散する油拡散部材を兼ねることで，専用の油拡散部材を不要として，構造の簡素化を図ることができる。 Further, since 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.
　さらにウエイト部１７は，その両端端部から凹部２１に向うに応じて第１遊星ギヤ１０の歯部に接近して凹部２１に達する一対の凹曲面２２Ａ，２２Ｂを内周に有するので，カウンタウエイト１５の回転方向の如何に拘らず，上記凹曲面２２Ａ，２２Ｂの何れか一方によりギヤケース１底部の貯留潤滑油Ｆａを掬い上げ，上記と同様の作用効果を達成することができる。 Further, 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.
　またウエイト部１７により掬い上げられて凹部２１へと誘導された潤滑油の他の一部は，アーム部１６の透孔２３から第１ケース半体１ａの内側面に向けて流出，拡散して，第２ボールベアリングＢ２を直接潤滑したり，第１ケース半体１ａ内側面の油受け凹部２６に受け入れられる。 Further, another part of the lubricating oil scooped up by the weight portion 17 and guided to the recess portion 21 flows out and diffuses from the through hole 23 of the arm portion 16 toward the inner surface of the first case half 1a. The second ball bearing B2 is directly lubricated or received in the oil receiving recess 26 on the inner surface of the first case half 1a.
　この油受け凹部２６に受け入れられた潤滑油は，下降通路２７を経て第１油溜め室２５へと流下して溜まり，第２ボールベアリングＢ２を潤滑しながら該ベアリングを通過し，第１油孔３１へと移行する。この間，潤滑油は，入力軸５から殆ど回転を受けないので，遠心力による逆流は生じない。しかも，第２ボールベアリングＢ２を通過した潤滑油は，油ガイド壁３２により，その内周面に連なる第１油孔３１へ誘導され，さらに油ブロック壁３３により第１油孔３１への流入が強制されることで，効率よく第１油孔３１を通過して偏心軸７の空洞部３０に流入する。 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. In addition, 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.
　尚，油ブロック壁３３を持たない環状の油ガイド壁３２を採用した場合には，第２ボールベアリングＢ２を通過した潤滑油は環状の油ガイド壁３２内に効率よく移り，そして遠心力により環状の油ガイド壁３２の内周面に押しつけられることで，環状の油ガイド壁３２の内周面に連なる第１油孔３１へ，次いで空洞部３０へと流れていく。 When the annular oil guide wall 32 having no oil block wall 33 is employed, 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. By being pressed against the inner peripheral surface of the oil guide wall 32, 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.
　こうして空洞部３０に流入した潤滑油は，直ちに環状溝３５に捕捉されると共に，偏心軸７の主軸線Ｘ１周りの公転により大なる遠心力を受けて，主軸線Ｘ１から離れる方向へ環状溝３５を流動するので，主軸線Ｘ１からの最遠位置もしくはその近傍位置で待機する第２油孔３６から第５及び第６ボールベアリングＢ５，Ｂ６間へ流出し，これらベアリングを潤滑する。 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.
　第５及び第６ボールベアリングＢ５，Ｂ６の潤滑後，これらベアリングを通過した潤滑油は，飛沫となって第１及び第２減速ギヤ列８，９を潤滑し，また偏心軸７の空洞部３０の開放口から流出した潤滑油も，飛沫となって第２減速ギヤ列９を潤滑する。 After the lubrication of the fifth and sixth ball bearings B5 and B6, 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.
　ところで，第１油溜め室２５に溜まる所定量以上の潤滑油は，第１オーバフロー通路２８よりギヤケース１の下部に流出する。これにより，第２ボールベアリングＢ２の潤滑に必要な所定量以上の潤滑油が第１油溜め室２５に溜まることが回避されるので，第２ボールベアリングＢ２の潤滑油による作動抵抗を小さく抑えると共に，ギヤケース１内での潤滑油の循環を良好にすることができる。また減速機Ｒの作動停止状態でも，第１油溜め室２５では所定量の潤滑油を溜め続けることができるので，減速機Ｒの作動開始時から第２ボールベアリングＢ２等の潤滑を行い得る利点もある。 Incidentally, 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. As a result, 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. In addition, even when the reduction gear R is stopped, a predetermined amount of lubricating oil can be continuously stored in the first oil sump chamber 25, so that the second ball bearing B2 and the like can be lubricated from the start of the reduction gear R operation. There is also.
　一方，カウンタウエイト１５により拡散された潤滑油や，偏心軸７の空洞部３０から流出した潤滑油が第２リングギヤ１４内に入ると，その一部の潤滑油は，前述のように第２減速ギヤ列９の噛合部の潤滑に供されるが，残余の潤滑油は，出力軸６のフランジ６ａの肉抜き孔３７を通過して第３ボールベアリングＢ３を潤滑し，そして該ベアリングを通過して第２油溜め室４０に溜まる。 On the other hand, when the lubricating oil diffused by the counterweight 15 or the lubricating oil flowing out from the hollow portion 30 of the eccentric shaft 7 enters the second ring gear 14, a part of the lubricating oil is second reduced as described above. Although used for lubricating the meshing portion of the gear train 9, the remaining lubricating oil passes through the lightening hole 37 of the flange 6a of the output shaft 6, lubricates the third ball bearing B3, and passes through the bearing. In the second oil sump chamber 40.
　この第２油溜め室４０でも，該室に溜まる所定量以上の潤滑油を，第２オーバフロー通路４１よりギヤケース１の下部に流出させることにより，第３ボールベアリングＢ３の潤滑に必要な所定量以上の潤滑油が溜まることを防ぐことができる。したがって第３ボールベアリングＢ３の潤滑油による作動抵抗を小さく抑えると共に，ギヤケース１内での潤滑油の循環を良好にすることができる。また第２油溜め室４０でも常時，所定量の潤滑油を溜め続けることができるので，減速機Ｒの作動開始時から第３ボールベアリングＢ３を潤滑することができる。 Also in 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.
　本発明の実施例２では，図８に示すように，カウンタウエイト１５のウエイト部１７の内周面に，その両端部から中央部に向かって深くなる樋状の凹部２１′が設けられ，この凹部２１′の最深部に，アーム部１６を貫通する透孔２３が開口する。その他の構成は実施例１と同様であり，図中，実施例１との対応部分には同一の符号を付して，重複する説明を省略する。 In the second embodiment of the present invention, as shown in FIG. 8, 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.
　この実施例２によれば，カウンタウエイト１５の回転により，ウエイト部１７がギヤケース１底部の貯留潤滑油Ｆａ（図３参照）を樋状の凹部２１により掬い上げたとき，その潤滑油が凹部２１からウエイト部１７の側方へ流出するのを極力抑えることができる。その結果，凹部２１に掬い上げられた潤滑油の多くは，アーム部１６の透孔２３から第１ケース半体１ａの内側面に向けて流出，拡散させるので，第２ボールベアリングＢ２に対する直接的潤滑，並びに油受け凹部２６への潤滑油の供給を効果的に行うことができる。 According to the second embodiment, when the counterweight 15 rotates, 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.
　尚，本発明は，上記実施例に限定されるものではなく，その要旨を逸脱しない範囲で種々の設計変更が可能である。例えば，上記実施例では，カウンタウエイト１５のウエイト部１７は，入力軸５の軸方向から見て左右対称形に形成してあるが，カウンタウエイト１５の重心Ｇ２が偏心回転体の重心Ｇ１と逆位相であれば，これを非対称形に形成してもよいことは勿論である。この場合，ウエイト部１７の凹部２１を，ウエイト部１７の内周面中央部よりウエイト部１７の回転方向後方側に配置して，凹曲面２２Ａを長く形成することにより，凹曲面２２Ａの貯留潤滑油Ｆａに対する掬い上げ距離を長くして，その潤滑油を第１遊星ギヤ１０の歯部に，より効果的に振りかけることができる。また遊星式減速機Ｒにおいて，遊星ギヤ及びリングギヤをサイクロイド歯形又は円弧歯形にする等，種々の歯形を採用することもできる。また出力軸６を入力軸，入力軸５を出力軸に変更すれば，減速機Ｒを増速機に変更することができる。 The present invention is not limited to the above embodiment, and various design changes can be made without departing from the scope of the invention. For example, in the above embodiment, 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. Of course, the phase may be asymmetrical. In this case, 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. In the planetary reduction gear R, 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.
　Ｂ２・・第１ベアリング（第２ボールベアリング）
　Ｂ５，Ｂ６・・第２ベアリング（第５及び第６ボールベアリング）
　Ｆ・・潤滑油
　Ｒ・・遊星式伝動装置（遊星式減速機）
　Ｘ１・・主軸線；Ｘ２・・偏心軸線
　１・・ギヤケース
　７・・偏心軸
　５・・伝動軸（入力軸）
　１０・・遊星ギヤ（第１遊星ギヤ）
　１１・・リングギヤ（第１リングギヤ）
　１５・・カウンタウエイト
　１６・・アーム部
　１７・・ウエイト部
　２３・・透孔
　２５・・油溜め室（第１油溜め室）
　２６・・油受け凹部
　２８・・オーバフロー通路（第１オーバフロー通路）
　３０，３１，３６・・油路（空洞部，第１油孔，第２油孔）
　３２・・油ガイド壁
　３３・・油ブロック壁 B2 ... First bearing (second ball bearing)
B5, B6 .. 2nd bearing (5th and 6th ball bearing)
F ・ ・ Lubricant R ・ ・ Planet type transmission (Planet type reduction gear)
X1 ··· Main axis; X2 · · Eccentric axis 1 · · Gear case 7 · · Eccentric shaft 5 · · Transmission shaft (input shaft)
10. Planetary gear (first planetary gear)
11. Ring gear (first ring gear)
15 ··· Counterweight 16 · · Arm portion 17 · · Weight portion 23 · · Through hole 25 · · Oil sump chamber (first oil sump chamber)
26 .. Oil receiving recess 28.. Overflow passage (first overflow passage)
30, 31, 36 .. Oil passage (cavity, first oil hole, second oil hole)
32 ... Oil guide wall 33 ... Oil block wall

Claims (7)

  1. 　ギヤケースと，該ギヤケースに第１ベアリングを介して回転自在に支持される伝動軸と，該伝動軸に一体的に結合される偏心軸と，該偏心軸の周壁に第２ベアリングを介して支持される遊星ギヤと，前記ギヤケースに前記伝動軸と同軸状に固定されるリングギヤとを備え，前記偏心軸の一側壁が前記第１ベアリングに対面している遊星式伝動装置における潤滑構造であって，
    　前記ギヤケースの底部に貯留される潤滑油と，
    　前記潤滑油を前記ギヤケース内に拡散させる油拡散部材と，
    　前記第１ベアリングの，前記偏心軸と反対側の側面に隣接するよう前記ギヤケースに設けられ，拡散した前記潤滑油を受容する油溜め室と，
    　前記偏心軸に，その前記一側壁及び前記周壁間を貫通するように設けられ，前記油溜め室から前記第１ベアリングを通過した潤滑油を前記第２ベアリングに供給する油路とを備えることを特徴とする，遊星式伝動装置における潤滑構造。     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 a peripheral wall of the eccentric shaft supported by a second bearing. A planetary gear having a planetary gear 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;
    Lubricating oil stored at the bottom of the gear case;
    An oil diffusion member for diffusing the lubricating oil into the gear case;
    An oil sump chamber provided in the gear case so as to be adjacent to a side surface of the first bearing opposite to the eccentric shaft, and receiving the diffused lubricating oil;
    An oil passage provided in the eccentric shaft so as to penetrate between the one side wall and the peripheral wall, and supplying lubricating oil that has passed through the first bearing from the oil reservoir chamber to the second bearing. Characteristic lubrication structure for planetary gearbox.
  2. 　請求項１に記載の遊星式伝動装置における潤滑構造であって，
    　前記偏心軸の前記一側壁には，転がり軸受よりなる前記第１ベアリングのアウタレースに近接して，該第１ベアリングを通過した潤滑油を前記油路の入口に誘導する油ガイド壁が連設される。     A lubricating structure for a planetary transmission device according to claim 1,
    An oil guide wall that guides the lubricating oil that has passed through the first bearing to the inlet of the oil passage is connected to the one side wall of the eccentric shaft in the vicinity of the outer race of the first bearing made of a rolling bearing. The
  3. 　請求項２に記載の遊星式伝動装置における潤滑構造であって，
    　前記油ガイド壁は，前記第１ベアリングのアウタレースに沿うように円弧状をなすと共に，該油ガイド壁の，前記伝動軸の回転方向後方側の一端に半径方向内方へ屈曲した油ブロック壁が連設され，これら油ガイド壁及び油ブロック壁間に前記油路の入口が開口する。     A lubricating structure for a planetary transmission device according to claim 2,
    The oil guide wall has an arc shape along the outer race of the first bearing, and an oil block wall bent radially inward at one end of the oil guide wall on the rear side in the rotation direction of the transmission shaft. The inlet of the oil passage opens between the oil guide wall and the oil block wall.
  4. 　請求項１～３の何れか１項に記載の遊星式伝動装置における潤滑構造であって，
    　前記ギヤケースの，前記油溜め室より上方の内側面に，前記油拡散部材に対面する油受け凹部が設けられ，該油受け凹部の下部が前記油溜め室に連通する。     A lubricating structure in a planetary transmission device according to any one of claims 1 to 3,
    An oil receiving recess facing the oil diffusion member is provided on the inner surface of the gear case above the oil sump chamber, and a lower portion of the oil receiving recess communicates with the oil sump chamber.
  5. 　請求項１～４の何れか１項に記載の遊星式伝動装置における潤滑構造であって，
    　前記油溜め室に溜まる所定量以上の潤滑油を前記ギヤケースの下部に流出させるオーバフロー通路が該油溜め室に接続される。     A lubricating structure in a planetary transmission device according to any one of claims 1 to 4,
    An overflow passage through which a predetermined amount or more of the lubricating oil stored in the oil reservoir chamber flows out to the lower portion of the gear case is connected to the oil reservoir chamber.
  6. 　請求項１～５の何れか１項に記載の遊星式伝動装置における潤滑構造であって，
    　前記油拡散部材が，前記伝動軸に結合されて，前記偏心軸及び遊星ギヤを含む偏心回転体の回転アンバランスを抑制するカウンタウエイトであり，
    　該カウンタウエイトは，前記第１ベアリングと前記偏心軸との間で前記伝動軸から半径方向に延出するアーム部と，該アーム部の先端部から前記遊星ギヤ及び前記リングギヤの噛合しない歯部間に張り出し，回転時，前記ギヤケースに貯留する前記潤滑油を掬い上げる内周面を持つウエイト部とを有する。     A lubricating structure in a planetary transmission device according to any one of claims 1 to 5,
    The oil diffusion member is coupled to the transmission shaft, and is a counterweight that suppresses rotational unbalance of an eccentric rotating body including the eccentric shaft and the planetary gear;
    The counterweight includes an arm portion extending radially from the transmission shaft between the first bearing and the eccentric shaft, and a tooth portion between the distal end portion of the arm portion and the planetary gear and the ring gear that are not meshed with each other. And a weight portion having an inner peripheral surface for scooping up the lubricating oil stored in the gear case during rotation.
  7. 　請求項６項に記載の遊星式伝動装置における潤滑構造であって，
    　前記アーム部には，その両側面を貫通して前記ウエイト部の内周面に連なる透孔が設けられる。     A lubricating structure for a planetary transmission device according to claim 6,
    The arm portion is provided with a through hole that penetrates both side surfaces thereof and continues to the inner peripheral surface of the weight portion.
PCT/JP2018/002818 2017-02-08 2018-01-30 Lubrication structure for planetary transmission device WO2018147120A1 (en)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008275094A (en) * 2007-05-01 2008-11-13 Ntn Corp In-wheel motor drive unit
JP2010203588A (en) * 2009-03-05 2010-09-16 Toyota Motor Corp Lubricating structure for planetary gear mechanism
JP2016114184A (en) * 2014-12-16 2016-06-23 Ntn株式会社 Cycloid speed reducer and in-wheel motor drive with cycloid speed reducer

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008275094A (en) * 2007-05-01 2008-11-13 Ntn Corp In-wheel motor drive unit
JP2010203588A (en) * 2009-03-05 2010-09-16 Toyota Motor Corp Lubricating structure for planetary gear mechanism
JP2016114184A (en) * 2014-12-16 2016-06-23 Ntn株式会社 Cycloid speed reducer and in-wheel motor drive with cycloid speed reducer

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