JP2018132181A - Eccentric oscillation type gear device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To supply a sufficient lubricant to the vicinity of eccentric body bearings to extend the life of a gear device.SOLUTION: An eccentric oscillation type gear device G1 comprises oscillation gears 11 and 12, and a crankshaft 14 that oscillates the oscillation gears, and also comprises a first gear 1 provided on the crankshaft, and a second gear 2 engaging with the first gear. The crankshaft comprises a first lubrication passage 81 provided in an axial direction of the crankshaft, and a second lubrication passage 82 communicating with the first lubrication passage and opening in outer peripheries 82A1 and 82B1 of the crankshaft. The first gear comprises a third lubrication passage 83 formed from the outer peripheral side of the first gear toward the inside. The crankshaft comprises a fourth lubrication passage 84 communicating with the first lubrication passage 81 and the third lubrication passage 83.SELECTED DRAWING: Figure 2

Description

  The present invention relates to an eccentric oscillating gear device.

  Patent Document 1 discloses an eccentric oscillating gear device. This gear device includes a swinging external gear and an internal gear with which the external gear is in mesh with the internal gear. The gear device takes out the relative rotation between the external gear and the internal gear obtained by eccentrically swinging the external gear as an output.

  Therefore, this gear device includes a crankshaft for swinging and rotating the external gear. The crankshaft includes an eccentric body having an eccentric center with respect to the crankshaft, and an external gear is swung via an eccentric body bearing incorporated in the outer periphery of the eccentric body.

JP 2014-206249 A (FIG. 1)

  The gear device disclosed in Patent Document 1 has a problem in that the life of the gear device is shortened unless sufficient lubricant is supplied to the vicinity of the eccentric bearing.

  The present invention has been made to solve the above-described conventional problems, and an object thereof is to supply a sufficient lubricant in the vicinity of the eccentric bearing so as to extend the life of the gear device.

  The present invention is an eccentric oscillating gear device including an oscillating gear and a crankshaft that oscillates the oscillating gear, the first gear provided on the crankshaft, and the first gear. A second gear that meshes with the gear, and the crankshaft communicates with the first lubrication passage provided in the axial direction of the crankshaft, and opens to an outer periphery of the crankshaft. A second lubricating passage, wherein the first gear has a third lubricating passage formed inwardly from the outer peripheral side of the first gear, and the crankshaft includes the first lubricating passage and the first lubricating passage. The above-described problem is solved by having a fourth lubrication passage communicating with the third lubrication passage.

  In the present invention, the first gear provided on the crankshaft and the second gear meshing with the first gear are utilized as a pump for supplying lubricant.

  For this purpose, the crankshaft first has a first lubrication passage provided in the axial direction of the crankshaft and a second lubrication passage that communicates with the first lubrication passage and opens to the outer periphery of the crankshaft. Yes. The first gear has a third lubrication passage formed inward from the outer peripheral side of the first gear, and the crankshaft communicates with the first lubrication passage and the third lubrication passage. have.

  Thus, the lubricant in the meshing portion between the first gear and the second gear is allowed to reach the outer periphery of the crankshaft through the third lubrication passage, the fourth lubrication passage, the first lubrication passage, and the second lubrication passage. Can do.

  According to the present invention, sufficient lubricant can be supplied near the eccentric body bearing, and the life of the gear device can be extended.

Sectional drawing which shows the whole structure of the eccentric rocking | fluctuation type gear apparatus which concerns on an example of embodiment of this invention. 1 is an enlarged cross-sectional view of the main part of FIG. Schematic sectional view showing the meshing relationship between the sorting gear and the input pinion of the gear device 3 is an enlarged cross-sectional view of the main part of FIG. Cross-sectional view perpendicular to the axis of the first eccentric body of FIG. Cross-sectional view perpendicular to the axis of the second eccentric body of FIG. Sectional drawing which shows the whole structure of the eccentric rocking | fluctuation type gear apparatus which concerns on other embodiment of this invention. 7 is an enlarged cross-sectional view of the main part of FIG. Sectional drawing which shows the whole structure of the eccentric rocking | fluctuation type gear apparatus which concerns on further another embodiment of this invention. 9 is an enlarged cross-sectional view of the main part of FIG.

  Hereinafter, examples of embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a cross-sectional view showing an overall configuration of an eccentric oscillating gear device according to an example of an embodiment of the present invention.

  The eccentric oscillating gear device G1 includes a first external gear 11 and a second external gear 12 as oscillating gears. The first external gear 11 and the second external gear 12 are swung by the crankshaft 14. The crankshaft 14 includes a first eccentric body 21 that swings the first external gear 11 and a second eccentric body 22 that swings the second external gear 12. A first eccentric body bearing 31 is disposed between the first eccentric body 21 and the first external gear 11. A second eccentric body bearing 32 is disposed between the second eccentric body 22 and the second external gear 12.

  The first external gear 11 and the second external gear 12 are in mesh with the internal gear 25 while swinging. The gear device G1 cranks the relative rotation of the first external gear 11 and the second external gear 12 and the internal gear 25 obtained by swinging the first external gear 11 and the second external gear 12. The first carrier 41 and the second carrier 42 supporting the shaft 14 are taken out.

  More specific description will be given below.

  In the gear device G <b> 1, the input shaft 24 is shared by the motor shaft of the motor 26. The input shaft 24 is disposed on the axis C25 of the internal gear 25. An input pinion (second gear) 2 is provided at the tip of the input shaft 24.

  The input pinion 2 meshes simultaneously with a plurality of (three in this example) sorting gears (first gears) 1. Each sorting gear 1 is provided (connected) at the end of the crankshaft 14 and can drive the crankshaft 14. In the gear device G1, the sorting gear 1 corresponds to a first gear provided at the end of the crankshaft 14, and the input pinion 2 corresponds to a second gear that meshes with the first gear.

  In other words, the gear device G1 includes a first gear provided on the crankshaft and a second gear that meshes with the first gear (contributing to power transmission from the input shaft to the output shaft) The input pinion 2 is used. Specific configurations of the sorting gear 1 and the input pinion 2 will be described in detail later.

  A plurality of crankshafts 14 (three in this example) are provided at positions offset from the axis C25 of the internal gear 25 by a distance L (C14-C25). The crankshaft 14 is integrally provided with a first eccentric body 21 and a second eccentric body 22 (a separate eccentric body is used as a crankshaft material using a key or the like as in a gear device G3 described later). It may be connected to form a crankshaft). Each crankshaft 14 passes through the first through hole 11 </ b> A of the first external gear 11 and the second through hole 12 </ b> A of the second external gear 12.

  The first eccentric body 21 and the second eccentric body 22 have axial centers C21 and C22 that are eccentric with respect to the axial center C14 of the crankshaft 14, respectively. The eccentric phase difference between the first eccentric body 21 and the second eccentric body 22 is 180 degrees (eccentric in a direction away from each other). The phases of the first eccentric bodies 21 at the same position in the axial direction of the crankshafts 14 are aligned. The phases of the second eccentric bodies 22 at the same position in the axial direction of the crankshafts 14 are also aligned.

  The first external gear 11 is incorporated in the outer periphery 21 </ b> A of the first eccentric body 21 via a first eccentric body bearing 31 so as to be able to swing eccentrically. The second external gear 12 is incorporated into the outer periphery 22A of the second eccentric body 22 via the second eccentric body bearing 32 so as to be capable of eccentric rocking (with an eccentric phase difference of 180 degrees from the first external gear 11). ing.

  The 1st eccentric body bearing 31 has the 1st roller 51 as a rolling element. The first eccentric body bearing 31 does not have independent inner and outer rings. The outer periphery 21 </ b> A of the first eccentric body 21 also serves as the inner ring (inner ring side rolling surface) of the first eccentric body bearing 31, and the first through hole 11 </ b> A of the first external gear 11 is the outer ring of the first eccentric body bearing 31 ( The outer ring side rolling surface is also used.

  The second eccentric body bearing 32 also has second rollers 52 as rolling elements. The second eccentric bearing 32 also has no independent inner ring and outer ring. The outer periphery 22 </ b> A of the second eccentric body 22 also serves as the inner ring (inner ring side rolling surface) of the second eccentric body bearing 32, and the second through hole 12 </ b> A of the second external gear 12 is the outer ring of the second eccentric body bearing 32. (Outer ring side rolling surface) is also used.

  The first external gear 11 and the second external gear 12 are in mesh with the internal gear 25. In this example, the internal gear 25 includes an internal gear main body 25A integrated with the casing 34, and a cylindrical internal tooth pin 25C rotatably incorporated in a groove 25B formed in the internal gear main body 25A. And comprising. The internal tooth pin 25 </ b> C constitutes an internal tooth of the internal gear 25. The number of internal teeth of the internal gear 25 (the number of internal pins 25C) is slightly smaller than the number of external teeth of the first external gear 11 and the second external gear 12 (only 1 in this example). Many.

  A first carrier 41 is disposed on the side of the first external gear 11 on the side opposite to the axial direction on the load side. A second carrier 42 is disposed on the side portion of the second external gear 12 on the axial load side. The crankshaft 14 is supported by the first carrier 41 via the first crankshaft bearing 61 and supported by the second carrier 42 via the second crankshaft bearing 62.

  The first carrier 41 and the second carrier 42 are connected via a carrier pin 44 and a carrier bolt 46 that protrude integrally from the second carrier 42 side. The carrier pin 44 penetrates the first external gear 11 and the second external gear 12 in a non-contact manner. The integrated first carrier 41 and second carrier 42 are supported by a roller bearing 71 and an output shaft bearing 72. An output shaft 54 is integrated on the load side of the second carrier 42. An output gear 56 is connected to the tip of the output shaft 54.

  In the case where the gear device G1 is placed vertically, the lubricant is sealed to such an extent that the lowermost end portion of the tooth portion of the input pinion 2 is immersed. Further, in the case of the horizontal placement, the lubricant is scraped up by the revolution of the sorting gear 1, so that the sealing may be at a lower level than the meshing portion 76 of the sorting gear 1 and the input pinion 2. Reference numerals 57 and 58 in FIG. 1 are oil seals.

  Here, before describing in detail the structure related to the lubrication of the present gear device G1, the operation of the gear device G1 relating to power transmission will be briefly described.

  When the input shaft 24 (motor shaft of the motor 26) rotates, the input pinion 2 of the gear device G1 rotates, and the three sorting gears 1 meshed simultaneously with the input pinion 2 have the same rotational speed in the same direction. Rotate with.

  As a result, the three crankshafts 14 rotate at the same speed in the same direction, and the first external gear 11 is provided via the first eccentric body 21 and the first eccentric body bearing 31 provided on each crankshaft 14. Oscillates, and the second external gear 12 oscillates via the second eccentric body 22 and the second eccentric body bearing 32. Since the number of teeth of the first external gear 11 and the second external gear 12 is one less than the number of teeth of the internal gear 25, the first external gear 11 and the second external gear 12 swing once. Each time it moves, it rotates relative to the internal gear 25 by one tooth (rotates).

  The rotation of the first external gear 11 and the second external gear 12 is transmitted to the crankshaft 14 that passes through the first external gear 11 and the second external gear 12, and the crankshaft 14 is transmitted through the first external gear 11. The first carrier 41 and the second carrier 42 supported via the crankshaft bearing 61 and the second crankshaft bearing 62 rotate. As the first carrier 41 and the second carrier 42 rotate, the output shaft 54 integrated with the first carrier 41 rotates, and the output gear 56 connected to the output shaft 54 rotates.

  Since the gear device G1 has such a power transmission structure, the first eccentric body bearing 31 and the second eccentric body bearing 32 are in a severe state in terms of strength, so that a sufficient amount of lubricant is supplied. Is needed. However, in reality, it was difficult to perform good lubrication in this portion because the lubricant is very difficult to enter and easily scatters due to centrifugal force. Therefore, in the gear device G1, the following configuration is adopted for the structure related to lubrication.

  2 is an enlarged cross-sectional view of the main part of FIG. 1, FIG. 3 is a schematic cross-sectional view showing the meshing relationship between the distribution gear 1 and the input pinion 2 of the gear device G1, and FIG. 4 is an enlarged cross-sectional view of the main part of FIG. FIG. 5 and 6 are cross-sectional views perpendicular to the axes of the first eccentric body 21 and the second eccentric body 22.

  As described above, the distribution gear 1 (first gear) is provided on the crankshaft 14 of the gear device G1. The gear device G1 has an input pinion 2 (second gear) that meshes with the sorting gear 1. The crankshaft 14 includes two first lubrication passages 81 provided in the axial direction of the crankshaft 14, and two discharge passages 82 </ b> A <b> 1 and 82 </ b> B <b> 1 that communicate with the first lubrication passage 81 and are provided on the outer periphery of the crankshaft 14. Second lubrication passage 82 (82A, 82B).

  Further, the distribution gear 1 has a third lubrication passage 83 formed from the outer periphery to the inner periphery of the distribution gear 1 (from the outer periphery side toward the inside), and the crankshaft 14 includes the first lubrication passage 81 and the first lubrication passage 81. The third lubrication passage 84 communicates with the third lubrication passage 83.

  Details will be described below.

  The crankshaft 14 has a first lubrication passage 81 provided in the axial direction of the crankshaft 14. Specifically, the first lubrication passage 81 passes through the crankshaft 14 in the axial direction at the position of the axis C14 of the crankshaft 14. Blocking plugs 53 and 55 are provided at both ends of the first lubrication passage 81, and the first lubrication passage 81 is isolated from the space around the crankshaft 14 in the gear device G1.

  The crankshaft 14 has two second lubrication passages 82 (82A, 82B) communicating with the first lubrication passage 81 at the first and second joining portions 64A, 64B. The second lubrication passages 82A and 82B have discharge openings 82A1 and 82B1 on the outer periphery of the crankshaft 14. In the gear device G1, two eccentric bodies, a first eccentric body 21 and a second eccentric body 22, are integrally provided on the crankshaft 14. The second lubrication passage 82 has the discharge openings 82A1 and 82B1 on the outer periphery 21A of the first eccentric body 21 and the outer periphery 22A of the second eccentric body 22, respectively.

  As described above, the “outer periphery of the crankshaft” in the second lubrication passage of the present invention includes “the outer periphery of the crankshaft” in addition to the literal “outer periphery of the crankshaft”. And the like exist in one body or separately, the concept of “the outer periphery of the eccentric body” is also included. In other words, whether or not the second lubrication passage is open to the outer periphery of the crankshaft (regardless of whether any component such as an eccentric body is provided integrally or separately on the outer periphery of the crankshaft). It may be open to the outer periphery of the component. Further, a member integrated on the outer periphery of the crankshaft can be regarded as a component of the crankshaft.

  As shown in FIG. 5, the second lubricating passage 82 </ b> A on the non-load side (input side) is located at the position of the first eccentric body 21 in the minimum eccentric direction 21 min in the circumferential direction of the crankshaft 14. It is formed along the radial direction and communicates with the first lubricating passage 81 and the first and second joining portions 64A. As shown in FIG. 6, the load-side (output-side) second lubrication passage 82 </ b> B has a diameter of the second eccentric body 22 at a position in the minimum eccentric direction 22 min of the second eccentric body 22 in the circumferential direction of the crankshaft 14. It is formed along the direction and communicates with the first lubricating passage 81 and the first and second joining portions 64B.

  Since the load is hardly applied in the minimum eccentric directions 21 min and 22 min, the discharge openings 82 </ b> A <b> 1 and 82 </ b> B <b> 1 of the second lubricating passage 82 are formed on the outer circumferences of the first eccentric body 21 and the second eccentric body 22. Therefore, a decrease in strength of the first eccentric body 21 and the second eccentric body 22 can be further reduced.

  On the other hand, the distribution gear 1 (first gear) provided at the end of the crankshaft 14 has a third lubrication passage 83 formed inwardly from the outer peripheral side of the distribution gear 1. As shown in FIG. 3, the third lubricating passages 83 are formed at intervals of 120 degrees in the circumferential direction, three for each sorting gear 1. More specifically, in this gear device G1, the crankshaft 14 has an outer spline 14A on the outer periphery of the axial end, and the sorting gear 1 is connected to an outer spline 14A provided on the outer periphery of the crankshaft 14. It has an inner spline 1B that engages. The third lubricating passage 83 has an inlet side opening 83A that opens to the root 1C of the external tooth 1A of the sorting gear 1, and an outlet side opening 83B that opens to the inner spline 1B. It penetrates radially from the side to the inside. Specifically, the inlet opening 83A of the third lubrication passage 83 is configured by an outer opening 74A of a check valve 73 described later.

  Further, the crankshaft 14 has a fourth lubrication passage 84 communicating with the first lubrication passage 81 and the third lubrication passage 83. Specifically, the fourth lubrication passage 84 is formed in the radial direction in the crankshaft 14. The fourth lubrication passage 84 has first to fourth joining portions 68 that communicate with the first lubrication passage 81 at one end, and communicates with the first lubrication passage 81. Further, the fourth lubrication passage 84 has an opposing opening 84A at a position facing the outlet opening 83B of the third lubrication passage 83 at the other end, and communicates with the third lubrication passage 83. Note that the vicinity of the opposed opening 84A of the fourth lubrication passage 84 is slightly expanded.

  In the third lubrication passage 83, a check valve 73 for preventing the flow of the lubricant from the inner circumference to the outer circumference (from the inside to the outside) of the sorting gear 1 is arranged. The check valve 73 includes a substantially cylindrical case 74, a closing ball 75, and a spring 77. The case 74 of the check valve 73 includes an outer opening 74A and an inner opening 74B at a cylindrical end. The outer opening 74 </ b> A also serves as the inlet opening 83 </ b> A of the third lubrication passage 83. A closing ball 75 urged by a spring 77 is in contact with the outer opening 74A, and the flow of the lubricant from the inner periphery to the outer periphery (from the inner side to the outer side) of the sorting gear 1 is prevented.

  The energizing force of the spring 77 of the check valve 73 is such that when the lubricant is fed from the outer circumference of the sorting gear 1 toward the inner circumference by the meshing of the input pinion 2 and the sorting gear 1, 75 is set to a strength capable of separating from the outer opening 74A.

  The check valve 73 may be disposed at any position of the third lubrication passage 83 or the fourth lubrication passage 84. However, preferably, the check valve 73 is preferably provided radially outside the center Cr83 in the radial direction of the third lubrication passage 83 in terms of efficiency. In the gear device G1, the check valve 73 is provided on the outermost side of the third lubrication passage 83 (position closest to the external tooth 1A of the sorting gear 1).

  A regulating member 78 that regulates the movement of the lubricant in the axial direction from the meshing portion 76 is disposed on one side (load side in this example) of the meshing portion 76 of the sorting gear 1 and the input pinion 2. Has been. This is because the amount of lubricant flowing into the third lubrication passage 83 decreases as the lubricant in the meshing portion 76 moves in the axial direction.

  The restricting member 78 is formed of a disk-shaped member, and in the gear device G1, is disposed between the collar 79 that restricts the axial movement of the first crankshaft bearing 61 and the sorting gear 1. . The outer diameter (radius) R78 of the regulating member 78 is larger than the shortest distance L (C14-2B) from the axis C14 of the crankshaft 14 to the root 2B of the outer teeth 2A of the input pinion 2. That is, the regulating member 78 closes the axial first external gear 11 side of the meshing portion 76 of the sorting gear 1 and the input pinion 2.

  On the other hand, if restricting members 78 that restrict the movement of the lubricant in the axial direction from the meshing portion 76 are arranged on both sides in the axial direction of the meshing portion 76, the lubricant itself entering the meshing portion 76 is reduced. In this gear device G1, from this point of view, the disk member 88 disposed on the side opposite to the first external gear in the axial direction does not close the meshing portion 76 (the lubricant can enter and exit the meshing portion 76).

  In addition, in the present gear device G1, the third lubricating passage 83 is positioned on the regulating member 78 side with respect to the axial center Ce1 of the sorting gear 1. Thereby, both the promotion of the inflow of the lubricant into the meshing portion 76 and the reduction of the outflow from the meshing portion 76 are achieved.

  Next, the flow of the lubricant in the gear device G1 will be described.

  FIG. 4 shows the structure of the meshing portion 76 between the sorting gear 1 and the input pinion 2. Now, it is assumed that the input pinion 2 is rotating in the clockwise direction in FIG. At this time, the volume of the space 85 between the external teeth 2 </ b> A of the input pinion 2 and the external teeth 1 </ b> A of the sorting gear 1 gradually decreases in the portion where engagement is about to start. At this time, the lubricant confined in the space 85 pushes the closing ball 75 of the check valve 73, and from the outer opening 74 </ b> A of the check valve 73 (part of the third lubricating passage 83). 73 enters the case 74.

  When the meshing is finished, the volume of the space 85 between the external teeth 2A of the input pinion 2 and the external teeth 1A of the sorting gear 1 increases, but at this time, the closed ball of the check valve 73 is closed. 75 maintains the outer opening 74 </ b> A in a closed state, so that no reverse flow of the lubricant from the third lubricating passage 83 occurs. Thus, in the vicinity of the inlet side opening 83A of the third lubrication passage 83 (outside opening 74A of the check valve 73), the external teeth 2A of the input pinion 2 and the external teeth 1A of the sorting gear 1 approach, mesh, and separate. Each time, the lubricant is sent into the third lubricating passage 83.

  The lubricant sent to the third lubrication passage 83 is sent to the fourth lubrication passage 84 via the opposed opening 84A of the fourth lubrication passage 84 facing the outlet opening 83B of the third lubrication passage 83. . At this time, part of the lubricant oozes into the engaging portion between the inner spline 1B of the sorting gear 1 and the outer spline 14A of the crankshaft 14, and contributes to prevention of fretting of the inner spline 1B and the outer spline 14A. To do.

  The lubricant sent to the fourth lubrication passage 84 is sent to the first lubrication passage 81 via the first to fourth joining portions 68, and further to two parts via the first to second joining portions 64A and 64B. It is fed into the second lubrication passages 82A and 82B. The second lubrication passages 82A and 82B open to the outer periphery of the crankshaft 14 (specifically, in this gear device G1, the outer periphery 21A of the first eccentric body 21 and the outer periphery 22A of the second eccentric body 22). Therefore, the lubricant that has flowed through the third lubrication passage 83, the fourth lubrication passage 84, the first lubrication passage 81, and the second lubrication passage 82 is discharged from the discharge openings 82A1, 82B1, and the first eccentric body. The vicinity of the bearing 31 and the second eccentric body bearing 32 is lubricated.

  In order to obtain this effect, the gear device G1 utilizes the distribution gear 1 provided on the crankshaft 14 as a first gear and the input pinion 2 that meshes with the distribution gear 1 as a second gear. That is, the existing distribution gear and the input pinion that contribute to power transmission from the input shaft to the output shaft are utilized. Therefore, there is an advantage that the number of parts does not increase and the existing casing 34 or the like can be used as it is.

  In addition to this basic action, the gear apparatus G1 can further obtain the following actions.

  In the gear device G1, a check valve 73 is provided on the outermost side of the third lubrication passage 83 (position closest to the external tooth 1A of the sorting gear 1). A closing ball 75 urged by a spring 77 abuts on the outer opening 74A of the check valve 73 to prevent the flow of lubricant from the inside to the outside of the sorting gear 1. That is, since the check valve 73 is provided on the outermost side of the third lubrication passage 83, the lubricant once fed into the third lubrication passage 83 may go out of the third lubrication passage 83 again. Absent. Therefore, the lubricant can be taken into the third lubricating passage 83 very efficiently.

  Note that the check valve 73 is not necessarily provided, and may not be provided. However, in order to obtain a more efficient pumping action, it is preferable to arrange the check valve 73. If the check valve 73 is disposed, the check valve 73 is preferably located in either the third lubrication passage 83 or the fourth lubrication passage 84, and more preferably in the radial direction with respect to the radial center Cr83 of the third lubrication passage 83. It is good to provide outside. As in the present gear device G1, it is most preferable to provide it on the outermost side of the third lubrication passage 83 (position closest to the external teeth 1A of the sorting gear 1) because the installation has the highest merit (high efficiency).

  In the present gear device G1, the lubricant is fed from the meshing portion 76 to the axial load side of the meshing portion 76 of the sorting gear 1 and the input pinion 2 on the axial load side (first external gear 11 side). A restricting member 78 that restricts the movement to the position is arranged. As a result, the lubricant generated by the meshing portion 76 can be prevented from leaking from the meshing portion 76 to the axial load side, and more lubricant can be guided to the third lubrication passage 83 side.

  Further, in the present gear device G1, since the regulating member 78 that regulates the movement of the lubricant from the meshing portion 76 to the axial load side is provided only on the axial load side of the sorting gear 1, the third gear device G1 is provided. The lubrication passage 83 is positioned closer to the regulating member 78 than the axial center Ce1 of the sorting gear 1.

  As a result, the lubricant can easily enter the meshing portion 76 from the side of the disk member 88 that does not close the meshing portion 76 and is disposed at a position close to the blocking regulating member 78. It is possible to efficiently enter the three lubrication passages 83.

  In addition, for example, when the regulating member capable of closing the meshing portion is not disposed on both sides in the axial direction of the meshing portion, or when the regulating member capable of closing the meshing portion is disposed on both sides in the axial direction of the meshing portion. The third lubricating passage may be arranged at the center in the axial direction of the sorting gear.

  7 and 8 show the overall configuration of an eccentric oscillating gear device G2 according to another embodiment of the present invention.

  7 and 8 show an eccentric oscillating gear having a crankshaft 114 that oscillates an external gear, which is a oscillating gear, on the axis of an internal gear 125 (a gear that meshes with the oscillating gear). An example in which the present invention is applied to the device G2 is shown.

  The crankshaft 114 also serves as the input shaft 124, and a shaft on the drive source side (not shown) is connected to the hollow portion 114H of the crankshaft 114 via a key or the like. The crankshaft 114 integrally includes a first eccentric body 121 and a second eccentric body 122 (with a single material). The axis C121 of the first eccentric body 121 and the axis C122 of the second eccentric body 122 are each eccentric by an eccentricity amount e with respect to the axis C114 of the crankshaft 114. A first external gear 111 is incorporated on the outer periphery 121 </ b> A of the first eccentric body 121 via a first eccentric body bearing 131. A second external gear 112 is incorporated on the outer periphery 122 </ b> A of the second eccentric body 122 via a second eccentric body bearing 132. Also in this gear device G2, the first eccentric body bearing 131 and the second eccentric body bearing 132 do not have dedicated inner and outer rings.

  The first external gear 111 and the second external gear 112 are in mesh with the internal gear 125. The internal teeth of the internal gear 125 are constituted by cylindrical internal teeth pins 125C. The number of internal teeth of the internal gear 125 (the number of internal teeth pins 125C) is one more than the number of external teeth of the first external gear 111 and the second external gear 112. A first carrier 141 and a second carrier 142 are disposed on both axial sides of the first external gear 111 and the second external gear 112. The first carrier 141 and the second carrier 142 are rotatably supported by the casing 134 via the first angular ball bearing 171 and the second angular ball bearing 172. The first carrier 141 and the second carrier 142 support the crankshaft 114 via the first ball bearing 161 and the second ball bearing 162.

  An inner pin 144 projects integrally from the load-side second carrier 142. A cylindrical inner roller 165 is fitted on the inner pin 144 as a sliding promotion member. The inner pin 144 and the inner roller 165 constitute a “pin-shaped member 165P”. The pin-shaped member 165P is disposed at a position offset from the axis C125 of the internal gear 125 by a distance L (C125-C165P), and the first inner roller hole 111A and the second inner roller hole 111A are formed in the first external gear 111. The second inner roller hole 112 </ b> A formed in the external gear 112 is penetrated.

  The inner roller 165 and the first inner roller hole 111 </ b> A are in contact with each other, and a gap corresponding to twice the eccentric amount e of the first eccentric body 121 is secured in a portion that does not contact. The inner roller 165 and the second inner roller hole 112A have the same configuration. In addition, the inner roller 165 which is a sliding acceleration | stimulation member is not necessary.

  In the gear device G2, the first external gear 111 and the second external gear 112 are swung by the rotation of the crankshaft 114 as the input shaft 124, and the relative rotation generated by the meshing with the internal gear 125 is changed to the first. It is taken out from the first carrier 141 and the second carrier 142 via a pin-like member 165P (inner pin 144 and inner roller 165) passing through the external gear 111 and the second external gear 112.

  The gear device G2 is a center gear (first gear) provided integrally with the crankshaft 114 between the first external gear 111 and the second external gear 112 in order to actively generate a lubricant flow. Gear) 101 and a planetary gear (second gear) 102 that meshes with the center gear 101. The planetary gear 102 is supported by the outer periphery of the inner roller 165 (the outer periphery of the pin-shaped member 165P), and revolves around the axis C114 of the crankshaft 114 while rotating around the axis C165P of the pin-shaped member 165P. The planetary gear 102 does not mesh with any gear other than the center gear 101.

  The crankshaft 114 has a first lubrication passage 181 provided in the axial direction of the crankshaft 114. The first lubrication passage 181 is formed from the axial end surface of the crankshaft 114 on the load side, and is formed to the middle of the crankshaft 114 in the axial direction (inside the first external gear 111) (having a bottom. , Not penetrating the crankshaft 114). A closing plug 155 is fitted into the opening of the first lubricating passage 181.

  The crankshaft 114 communicates with the first lubrication passage 181 and has an outer periphery of the crankshaft 114 (more specifically, an outer periphery 121A of the first eccentric body 121 and an outer periphery 122A of the second eccentric body 122 integrated with the crankshaft 114). ) Have two second lubricating passages 182A and 182B.

  The center gear 101 has a third lubricating passage 183 formed from the outer periphery to the inner periphery of the center gear 101 (from the outer periphery toward the inner side). The crankshaft 114 has a fourth lubrication path 184 that communicates with the first lubrication path 181 and the third lubrication path 183. In the gear device G2, the center gear 101 is integrated with the crankshaft 114 (with a single material). Therefore, the third lubrication passage 183 of the center gear 101 and the fourth lubrication passage 184 of the crankshaft 114 are apparently continuous as one lubrication passage.

  Also in this gear device G2, a check valve that blocks the flow of lubricant from the inside to the outside of the center gear 101 on the outermost side of the third lubrication passage 183 (position closest to the outer teeth 101A of the center gear 101). 173 is arranged. The specific configuration of the check valve 173 is the same as that of the previous embodiment.

  Note that the gear unit G2 is filled with lubricant to such an extent that the lowermost end portion of the tooth portion of the center gear 101 is immersed. However, since the planetary gear 102 is swung up by the revolution of the planetary gear 102, a lower level may be sufficient if the planetary gear 102 is immersed.

  Similarly to the previous embodiment, the gear device G2 also causes the lubricant flow generated by the meshing of the center gear 101 and the planetary gear 102 to flow through the third lubricating passage 183, the fourth lubricating passage 184, the first lubricating passage 181, And it can be made to discharge from discharge opening part 182A1 and 182B1 of the outer periphery (the outer periphery 121A of the 1st eccentric body 121, and the outer periphery 122A of the 2nd eccentric body 122) of the crankshaft 114 via 2nd lubrication channel | path 182A, 182B. Thereby, the 1st eccentric body bearing 131 and the 2nd eccentric body bearing 132 can be forcedly lubricated.

  As described above, the planetary gear 102 of the gear device G2 does not mesh with any gear other than the center gear 101. That is, neither the center gear 101 nor the planetary gear 102 in the gear device G2 contributes to power transmission from the input shaft 124 to the output shaft (second carrier 142) of the gear device G2.

  Therefore, neither the center gear 101 nor the planetary gear 102 is required to have high strength, and the planetary gear 102 may be made of a non-metallic material such as resin. In addition, since the center gear 101 and the planetary gear 102 are gears provided for the purpose of improving lubrication, for example, the module is set to be larger or formed with a non-involute tooth profile (for example, a trochoidal tooth profile). Thus, the tooth profile can be designed with a focus on “pump performance”, and more efficient lubricant supply can be achieved.

  Further, the center gear 101 and the planetary gear 102 for taking in the lubricant are between the first external gear 111 and the second external gear 112, and the meshing portion 176 of the center gear 101 and the planetary gear 102 and the lubricant are discharged. The discharge openings 182A1 and 182B1 of the second lubrication passage 182 are adjacent to each other. Therefore, the overall length of the lubrication passage is short. Further, since the third lubrication passage 183 and the fourth lubrication passage 184 are integrated, a loss in the flow of the lubricant when reaching the fourth lubrication passage 184 from the third lubrication passage 183 is unlikely to occur. Therefore, more efficient lubricant supply is possible.

  7 and 8, the center gear 101 is integrally formed with the crankshaft 114 (by a single material). However, the center gear 101 is separate from the crankshaft 114. You may comprise with the material of. In this case, the crankshaft 114 and the center gear 101 may be connected by a spline. When the center gear 101 is configured by a member separate from the crankshaft 114, both the center gear 101 and the planetary gear 102 can be configured by resin (non-metallic material).

  9 and 10 show an eccentric oscillating gear device G3 according to still another embodiment of the present invention.

  This gear device G3 also has a crankshaft 214 on the axis of the internal gear 225 and a pin-like member 265P (internal pin 244 and internal roller 265) that penetrates the first external gear 211 and the second external gear 212. ), The relative rotation of the first external gear 211, the second external gear 212, and the internal gear 225 is taken out. The basic structure of the gear device G3 is the same as that of the gear device G2 shown in FIGS. Therefore, in FIGS. 9 and 10, the lower two digits are assigned the same reference numerals to the portions corresponding to the gear device G <b> 2 of FIGS. 8 and 9, and redundant description regarding the basic structure is omitted.

  In the gear device G3 shown in FIGS. 9 and 10, the crankshaft 214 also serves as the input shaft 224. The first eccentric body 221 and the second eccentric body 222 are formed on an eccentric body member 223 that is separate from the crankshaft 214. The eccentric body member 223 is connected to the crankshaft 214 by a key 215. The center gear (first gear) 201 is provided on the opposite load side (motor 226 side) of the crankshaft 214 (input shaft 224) via the same key 215.

  An idle gear (second gear) 202 that meshes with the center gear 201 is rotatably provided on a support shaft 204 that protrudes from the casing 234. Reference numeral 206 denotes a stop washer. The crankshaft 214 is solid.

  One first lubricating passage 281 is formed at the radial center of the crankshaft 214. The first lubrication passage 281 is drilled (with a bottom) from the end face on the axial load side of the crankshaft 214, and a closing plug 255 is attached to the opening.

  Since the first eccentric body 221 and the second eccentric body 222 are separately provided on the outer periphery of the crankshaft 214, the second lubricating passages 282A and 282B extend beyond the outer periphery 214A of the crankshaft 214 itself, and further Through the first eccentric body 221 and the second eccentric body 222, the discharge openings 282A1 and 282B1 of the second lubrication passages 282A and 282B open to the outer periphery 221A of the first eccentric body 221 and the outer periphery 222A of the second eccentric body 222. doing.

  The center gear 201 has a third lubricating passage 283 formed from the outer peripheral side of the center gear 201 toward the inside. The crankshaft 214 has a fourth lubrication passage 284 that communicates with the first lubrication passage 281 and the third lubrication passage 283. The third lubrication passage 283 and the fourth lubrication passage 284 are formed in a portion where the key 215 does not exist in the circumferential direction and communicate with each other.

  Also in this gear device G3, a check valve 273 is provided at the radially outermost position of the third lubricating passage 283. A plurality of second lubrication passages 282, third lubrication passages 283, and fourth lubrication passages 284 may be formed.

  In the gear device G3, neither the center gear 201 nor the idle gear 202 contributes to power transmission from the input shaft 224 to the output shaft 254 of the gear device G3. Therefore, both the center gear 201 and the idle gear 202 are made of resin (non-metallic material), and have a module and a tooth profile specialized for pump performance. Therefore, high pump performance can be secured at a small additional cost.

  Further, the idle gear 202 is arranged on the lower side in the vertical direction of the center gear 201. Thereby, while being able to reduce the quantity of the lubricant enclosed in the gear apparatus G3, the stirring resistance of the lubricant can be reduced. The gear unit G3 is filled with lubricant to such an extent that the lowermost end of the tooth portion of the idle gear 202 is immersed.

  The example of the three gear devices G1 to G3 has been described above as the configuration example of the first gear and the second gear. However, the configuration example of the first gear and the second gear according to the present invention is limited to these three configuration examples. Is not to be done.

  For example, in the above configuration examples, the first gear provided on the crankshaft is fixed to the crankshaft in the circumferential direction by spline connection or a single material. However, when rotational power is obtained from the second gear side, the first gear may be externally fitted on the outer periphery of the crankshaft.

  For example, in the gear device G1 shown in FIGS. 1 to 6, a second gear that rotates integrally with the input shaft 24 and functions as the second gear is provided in parallel with the input pinion 2 (aside from the input pinion 2). . Then, the first gear (having the third lubrication passage 83) that meshes with the second gear and functions as the first gear is parallel to the original distribution gear (without the third lubrication passage). The outer periphery of the shaft 14 is fitted (without a connecting spline).

  In this case, for example, if the gear ratio (reduction ratio) of the input pinion and the distribution gear contributing to power transmission is matched with the gear ratio (reduction ratio) of the second gear and the first gear, The original sorting gear and the first gear are rotated at the same rotational speed. That is, the crankshaft and the attached first gear rotate substantially integrally. Accordingly, since the correspondence relationship in the circumferential direction between the third lubrication passage provided in the first gear and the fourth lubrication passage provided in the crankshaft is not broken, the third lubrication passage and the fourth lubrication passage can be easily communicated. it can.

  According to this configuration, both the first cogwheel and the second cogwheel do not contribute to the power transmission of the gear device, and therefore both can be formed of a non-metallic material such as resin, thereby suppressing an increase in processing cost. be able to. Moreover, since it can be set as the module and tooth profile specialized in pump performance, high pump performance can be maintained. Further, in this configuration, the inner spline 1B and the outer spline 14A that existed in the gear device G1 exist between the first gear and the crankshaft (between the third lubrication passage and the fourth lubrication passage). Therefore, it is possible to further prevent the lubricant from leaking in the axial direction from the communication portion between the third lubrication passage and the fourth lubrication passage. Therefore, the lubricant can be sent to the first lubrication passage side more efficiently.

  In the configuration in which the first gear is externally fitted to the crankshaft, when the first gear and the crankshaft cannot be rotated at the same rotational speed by a technique such as adjustment of the reduction ratio, the circumferential direction of the crankshaft is, for example, The third lubrication passage and the fourth lubrication passage can be communicated with each other by, for example, forming a groove that makes one round. Thus, the first gear provided on the crankshaft is not necessarily fixed to the crankshaft in the circumferential direction.

  As already described, the second lubrication passage in the present invention (whether or not any component such as an eccentric body is provided integrally or separately on the outer periphery of the crankshaft) You may open to the outer periphery and you may open to the outer periphery of the said some component. In the above-described embodiment, the second lubrication passage is open to the outer periphery of the eccentric body provided on the outer periphery of the crankshaft. For example, the second lubrication passage is between the eccentric body and the eccentric body or between the eccentric body and the crankshaft bearing. It may open to the outer periphery of the crankshaft.

  Moreover, in the said embodiment, the eccentric rocking | fluctuation type gear apparatus of the type with which an external gear rock | fluctuates is shown. However, among the eccentric oscillating gear devices, an internal oscillating type eccentric oscillating gear device in which an internal gear oscillates with respect to an external gear by a crankshaft is also known. The present invention can be similarly applied to the eccentric oscillating gear device of this type, and the same operational effects can be obtained.

  In each configuration example, the number of first to fourth lubrication passages to be formed is not particularly limited to the above configuration example (for example, a larger number of lubrication passages may be formed).

G1 ... Gear device 1 ... Distributing gear (first gear)
2 ... Input pinion (second gear)
11 ... 1st external gear (oscillating gear)
12 ... Second external gear (oscillating gear)
DESCRIPTION OF SYMBOLS 14 ... Crankshaft 81 ... 1st lubrication path 82 ... 2nd lubrication path 83 ... 3rd lubrication path 84 ... 4th lubrication path

Claims (9)

An eccentric oscillating gear device comprising an oscillating gear and a crank shaft for oscillating the oscillating gear,
A first gear provided on the crankshaft;
A second gear meshing with the first gear,
The crankshaft has a first lubrication passage provided in the axial direction of the crankshaft, and a second lubrication passage communicating with the first lubrication passage and opening to the outer periphery of the crankshaft,
The first gear has a third lubricating passage formed inward from the outer peripheral side of the first gear,
The crankshaft has a fourth lubrication passage communicating with the first lubrication passage and the third lubrication passage. The eccentric oscillating gear device according to claim 1,
An eccentric oscillating gear device, wherein the third lubrication passage or the fourth lubrication passage is provided with a check valve that prevents the flow of lubricant from the inside to the outside of the first gear. The eccentric oscillating gear device according to claim 2,
The eccentric oscillating gear device, wherein the check valve is provided radially outward from a radial center of the third lubrication passage. In the eccentric rocking | fluctuation type gear apparatus in any one of Claims 1-3,
An eccentric oscillating type comprising a regulating member disposed on an axial side portion of the meshing portion of the first gear and the second gear and regulating the lubricant from moving in the axial direction from the meshing portion. Gear device. The eccentric oscillating gear device according to claim 4,
The eccentric oscillating gear device, wherein the third lubrication passage is located closer to the regulating member than an axial center of the first gear. In the eccentric rocking | fluctuation type gear apparatus in any one of Claims 1-5,
At least one of the first gear and the second gear is a gear that does not contribute to power transmission from the input shaft to the output shaft of the eccentric oscillating gear device.
An eccentric oscillating gear device. The eccentric oscillating gear device according to claim 6,
The gear that does not contribute to power transmission is made of a non-metallic material. The eccentric oscillating gear device according to claim 6 or 7,
An external gear that functions as the oscillating gear, an internal gear with which the external gear meshes internally, and a pin-like member that penetrates the external gear,
The crankshaft is disposed on an axis of the internal gear;
The first gear is composed of a gear that rotates together with the crankshaft,
The second gear is constituted by a planetary gear supported by the pin-shaped member. The eccentric oscillating gear device according to claim 6 or 7,
The first gear is composed of a gear that rotates together with the crankshaft,
The eccentric oscillating gear device, wherein the second gear is an idle gear that meshes with the first gear.

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