JP2011043243A - Power transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a swinging inscribed meshing type power transmission device which allows for efficient lubrication and cooling of a contact surface between an eccentric body bearing and an eccentric body while maintaining the durability of constituent members. <P>SOLUTION: Oil blow-out openings 170A and 170B are formed toward the contact surfaces 174A and 174B with the eccentric body bearings 136A and 136B, respectively, from a hollow part 172 of a high speed shaft 132 which is integrally formed with the eccentric bodies 134A and 134B and which has the hollow part 172 into which a lubricating oil can flow. Moreover, the oil blow-out openings 170A and 170B are provided in the opposite directions (the direction where the load from the eccentric body is relatively lessened) for the eccentricity of the eccentric bodies 134A and 134B, respectively. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a swinging intermeshing type power transmission device.

  As described in Patent Document 1, a swinging internal meshing type power transmission device using an internal gear and an external gear is conventionally known.

  FIG. 8 is a side sectional view of the power transmission device 10 described in Patent Document 1. As shown in FIG.

  As shown in FIG. 8, an eccentric body 34 is integrated with the high-speed shaft 32 by a key 35, and an eccentric body bearing 36 is disposed around the eccentric body 34. The eccentric bearing 36 is fitted to an external gear 38 so that the external gear 38 can swing. The external gear 38 is provided with a plurality of inner pin holes 39, and the inner pins 42 and the inner rollers 44 are loosely fitted in the inner pin holes 39. One end of the inner pin 42 is engaged with the output flange 58. The output flange 58 is formed integrally with the low speed shaft 22.

  The external gear 38 meshes with the external pin 40.

  FIG. 9 is a cross-sectional view of the eccentric bearing 36 along the line IX-IX in FIG. As shown in FIG. 9, the retainer (retainer) 76 provided in the eccentric body bearing 36 is not between the rollers (rolling bodies) 37, but in the radial direction of the rollers 37 arranged around the eccentric body 34. Arranged outside. Accordingly, a bearing (eccentric bearing) can be configured by reducing the gap ΔL2 between the rollers. By comprising in this way, the number of rollers can be increased and the load capacity of an eccentric body bearing can be enlarged.

  During operation, as the high-speed shaft 32 rotates at high speed, the eccentric body 34 rotates eccentrically, and the external gear 38 is swung at high speed via the eccentric body bearing 36. At this time, since the eccentric body bearing 36 rolls and slides while being in contact with the eccentric body 34 and the external gear 38, lubrication with a lubricating oil (lubricant) is required to ensure the durability of each member.・ Cooling is required. Therefore, lubricating oil corresponding to the application is sealed inside the power transmission device.

JP 2004-84948 A

  However, in the conventional power transmission device, there are cases where the eccentric body bearing portion is not always sufficiently lubricated and cooled. In particular, the retainer provided in the eccentric body bearing is disposed on the radially outer side of the rollers arranged circumferentially around the eccentric body, and the gap between the rollers is as small as possible (to ensure load capacity). When configured, even if lubricating oil is supplied to the radially outer side (retainer side) of the eccentric body bearing, the presence of the rollers blocks the arrival of the lubricating oil radially inward, and the eccentric body bearing and the eccentric body Lubrication / cooling of the contact surface (radial inner contact surface of the eccentric bearing) may be insufficient.

  Further, since the entire eccentric body bearing is eccentrically rotated at a high speed, even if the lubricating oil is supplied to the outer side in the radial direction of the eccentric body bearing, the lubricating oil is blown off by the centrifugal force and reaches the inner side in the radial direction. Is difficult.

  Accordingly, the present invention provides a swinging intermeshing type power transmission device capable of efficiently performing lubrication and cooling of the contact surface between the eccentric bearing and the eccentric body while maintaining the durability of the constituent members. The task is to do.

  The present invention provides an internal gear, an external gear that has a slight difference in the number of teeth from the internal gear and that meshes internally with the internal gear, and swings the external gear via a bearing. An eccentric body, the eccentric body having a hollow portion into which lubricating oil can flow, and an oil outlet hole penetrating from the hollow portion to a contact surface of the eccentric body with the bearing. Therefore, the above problem is solved.

  The above configuration is that the load applied to the eccentric body by the inventor is not constant in the circumferential direction, is always large in a specific direction (range) in relation to the eccentric direction, and the others are not applied so much or not at all. It is the result of paying attention to.

  That is, the oil outlet that can supply the lubricating oil according to the centrifugal force from the inner side to the outer side in the radial direction is formed in a direction in which the load from the bearing is relatively small.

  Thereby, durability of the site | part which formed the oil blower outlet is not impaired. Further, since the lubricating oil can be supplied according to the centrifugal force of the eccentric body that rotates eccentrically at high speed, the lubricating oil can be sufficiently supplied also to the contact surface between the eccentric body bearing and the eccentric body.

  It should be noted that the “portion where the load from the bearing is relatively large” without forming the oil outlet is the maximum load that can be applied from the eccentric pair bearing to the eccentric body during operation under a certain condition ( It means a contact surface on which a load of, for example, about 50% or more is applied with reference to the maximum load). The numerical value of “about 50%” can vary depending on the structure of the power transmission device.

  By applying the present invention, it is possible to efficiently lubricate and cool the contact surface between the eccentric body bearing and the eccentric body in the swinging intermeshing type power transmission device while maintaining the durability of the constituent members. It becomes possible.

Side sectional view of geared motor GM110 provided with a power transmission device as an example of an embodiment of the present invention. Front view of the same geared motor GM110 Enlarged view near arrow III in Figure 1 Sectional view along arrow IV-IV in FIG. It is a figure of the oil guide plate alone, (A) is a front view, (B) is a side view. Side sectional view of geared motor GM610 provided with a distribution type power transmission device which is another example of the embodiment of the present invention. Enlarged view near arrow VII in FIG. Side sectional view of the power transmission device 10 described in Patent Document 1 Sectional view of the eccentric bearing along the line IX-IX in FIG.

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

  First, a geared motor GM110 using a power transmission device 112, which is an example of an embodiment of the present invention, will be described with reference to FIGS.

  The geared motor GM110 is configured by connecting a motor 114 as a power source to a power transmission device 112. The power transmission device 112 according to the present embodiment is specifically configured as a speed reducer.

  The power transmission device 112 includes a high speed shaft 132, a speed change mechanism K1, and a low speed shaft 122.

  The speed change mechanism K1 includes eccentric bodies 134A and 134B, eccentric body bearings 136A and 136B, external gears 138A and 138B, internal pin holes 139A and 139B, an external pin 140, an internal gear 141, an internal pin 142, and an internal roller. 144. The outer pin 140 is a member that functions as a tooth of the internal gear 141.

  The power transmission device 112 includes a casing body 116 that also functions as an internal gear 141, a donut-shaped front cover 117 that is fixed to the casing body 116 with bolts 120, and an end cover 118 that is fixed with bolts 119. Is further provided. In the present embodiment, the end cover 118 and the casing of the motor 114 are integrally formed, but the present invention is not limited to this. Further, a low speed shaft 122 protrudes from a substantially central portion of the front cover 117 and can rotate around the axis O1. Further, this rotation can be transmitted to a partner machine (not shown).

  Inside the power transmission device 112, the motor shaft 115 of the motor 114 faces. The motor shaft 115 is fitted in the hollow portion 172 of the high speed shaft 132. That is, one of the hollow high-speed shafts 132 is covered with the motor shaft 115 fitted therein. In addition, although the code | symbol is not attached | subjected to this fitting part of the motor shaft 115 and the high-speed shaft 132, each spline is provided and it has mutually meshed | engaged and the rotation of the motor shaft 115 is transmitted to the high-speed shaft 132 Possible configuration. The high-speed shaft 132 is supported by bearings 128 and 130, and is rotatable about the axis O1.

  First and second eccentric bodies 134A and 134B are integrally formed on the high-speed shaft 132. In the present embodiment, the first and second eccentric bodies 134A and 134B are formed eccentrically by Δε from the axial center O1 at different positions in the axial direction of the high-speed shaft 132 with a 180 ° phase difference. Of course, the number of the eccentric bodies may be one, or three or more according to the number of external gears. The first and second eccentric bodies 134A and 134B are fitted to the first and second external gears 138A and 138B via first and second eccentric body bearings 136A and 136B, respectively.

  The eccentric body bearings 136A and 136B include a plurality of first and second rollers (rolling elements) 137A and 137B arranged circumferentially around the eccentric bodies 134A and 134B, and first and second retainers 176A, 176B. As is clear from FIG. 4, the retainers 176A and 176B are arranged and configured to be positioned radially outside the rollers 137A and 137B arranged circumferentially. The gaps between 137B are arranged close together (to ensure the load capacity). Each external gear 138A, 138B meshes with an external pin 140 corresponding to the tooth of the internal gear 141. There is a slight difference between the number of outer pins 140 and the number of teeth of the external gears 138A and 138B.

  Each external gear 138A, 138B is provided with a plurality of inner pin holes 139A, 139B, and the inner pin 142 and the inner roller 144 are loosely fitted in these inner pin holes 139A, 139B. Both ends of the inner pin 142 are fitted to the first and second output flanges 156 and 158, and the rotation components of the external gears 138A and 138B, that is, the internal gear 141 and the external gears 138A and 138B. The decelerated rotation generated by the meshing can be transmitted to the output flanges 156 and 158. Note that the output flanges 156 and 158 and the high-speed shaft 132 are in contact with each other via bearings 128 and 130, and therefore can rotate independently of each other.

  The second output flange 158 is formed integrally with the low speed shaft 122 and can transmit the reduced speed rotation (rotation of the external gear) to a counterpart machine (not shown). A donut-shaped oil guide plate 152 (see FIG. 5) is fixed to the second output flange 158 with bolts 150. The oil guide plate 152 is provided with a plurality of scooping portions 154 formed on the oil guide plate in a substantially vertical direction, and is enclosed in the power transmission device as the second output flange 158 rotates. It is possible to scoop up lubricating oil.

  Further, the second output flange is provided with an oil guide hole 160 that can carry the lubricating oil pumped up by the oil guide plate 152 in the axial direction. Further, the second output flange 158 is provided with a hollow cylindrical return oil guide 162 fitted in the hollow portion 172 of the high-speed shaft 132 (on the opposite side in the axial direction where the motor shaft 115 is fitted). .

  Also, the first and second oils from the hollow portion 172 of the high-speed shaft 132 integrally formed with the eccentric bodies 134A and 134B toward the contact surfaces 174A and 174B of the eccentric bodies 134A and 134B with the eccentric body bearings 136A and 136B. Air outlets 170A and 170B are formed. In this embodiment, as is apparent from FIGS. 3 and 4, the oil outlets 170A and 170B are provided at one place in the anti-eccentric direction (position 180 degrees from the eccentric direction) of the eccentric bodies 134A and 134B. ing. However, the present invention is not limited to this, as long as it is provided within a range of ± 15 degrees with respect to the anti-eccentric direction or within a range of ± 15 degrees with respect to the eccentric direction. May be. The power transmission device can be changed as appropriate according to the capacity and usage status of the power transmission device, the lubricating oil used, and the like.

  1 and 2, reference numeral 121 denotes a lid for the lubricating oil inlet, and a hole 151 provided in the oil guide plate 152 in FIG. 5 is a hole through which the bolt 150 passes.

  FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG. 1. In FIG. 1 and FIG. 4, the rotational position of the eccentric body 134A is slightly different.

  Next, the operation of the geared motor GM110 will be described.

  When the motor 114 is energized, the motor shaft 115 rotates accordingly. Such rotation is transmitted to the high-speed shaft 132, and the eccentric bodies 134A and 134B are eccentrically rotated. This rotation causes the external gears 138A and 138B to swing and rotate via the eccentric bearings 136A and 136B. However, since the external gears 138A and 138B are in mesh with the external pins 140, the external gears 138A and 138B are substantially swung while rotating only by the difference between the number of external pins 140 and the number of teeth of the external gears 138A and 138B. Will only do.

  The swinging component of the external gear is absorbed by the inner pin 142 and the inner roller 144 that are loosely fitted in the inner pin holes 139A and 139B of the external gears 138A and 138B, and only the rotation component is transmitted through the inner pin 142. 1, transmitted to the second output flange 156, 158. At this time, the rotational speed of the high-speed shaft 132 is a rotational speed reduced to (number of external pins−number of teeth of external gear) / (number of teeth of external gear). This rotation is transmitted from the second output flange 158 to the low speed shaft 122, and can drive an unillustrated counterpart machine.

  Further, as the second output flange 158 rotates, the oil guide plate 152 fixed to the second output flange also rotates. Then, each lifting part 154 of the oil guide plate 152 sequentially lifts the lubricating oil (not shown) enclosed in the power transmission device 112, and the rising lubricating oil has an axial center from the vicinity of the lifting part 154. It flows through the oil guide hole 160 formed in the O1 direction and flows into the hollow portion 172 side of the high speed shaft 132. Here, since the high-speed shaft 132 rotates at a high speed, the lubricating oil that has flowed into the hollow portion 172 is given a centrifugal force (centrifugal force that tends to go radially outward from the axis O1). That is, through the oil outlets 170A and 170B formed in the high speed shaft 132, the lubricating oil is supplied to the contact surfaces 174A and 174B of the eccentric bodies 134A and 134B with the eccentric body bearings 136A and 136B. The lubricating oil supplied at this time is lifted up from the lower side in the power transmission device 112 by the oil guide plate 152 and supplied, and the temperature of the lubricating oil present in the device is relatively low. Since it is lubricating oil, the contact surfaces 174A and 174B that roll and slide at high speed can be effectively cooled.

  Further, since the return oil guide 162 formed on the second output flange 158 is fitted in the hollow portion 172, the lubricating oil flowing into the hollow portion 172 is prevented from immediately flowing out to the outside. Lubricating oil that can be supplied to each of the oil outlets 170A and 170B can be sufficiently secured in the hollow portion.

  In the present embodiment, since the oil outlets 170A and 170B are formed in the respective anti-eccentric directions of the eccentric bodies 134A and 134B, the drilling lengths of the oil outlets 170A and 170B can be shortened. Is also easy. Further, since the length is short, the lubricating oil is supplied more quickly.

  Furthermore, in the case of this embodiment, the eccentric body bearings 134A and 134B are subjected to a maximum load in the vicinity of 45 degrees with respect to the eccentric direction. Since the load from the eccentric bearings 134A and 134B is relatively small in the anti-eccentric direction, even if the oil outlets 170A and 170B are provided, the durability of the member is not sacrificed. This effect can be obtained substantially in the same manner when the oil outlets 170A and 170B are formed within a range of ± 15 degrees with respect to the anti-eccentric direction.

  On the other hand, although not implemented in the present embodiment, the oil outlets 170A and 170B may be formed in the eccentric direction. In this case, since the oil outlets 170A and 170B are formed in the portions where the thicknesses of the eccentric bodies 134A and 134B are the maximum, even if drilling is performed, the members can be formed without reducing the durability. Also, the load from the eccentric bearing is relatively small. This effect can be obtained in the same manner even when the oil outlets 170A and 170B are formed within a range of ± 15 degrees with respect to the eccentric direction.

  Further, one or more oil outlets may be formed in the range of ± 15 degrees from the anti-eccentric direction and in the range of ± 15 degrees from the eccentric direction. This makes it possible to supply more lubricating oil to the contact surfaces 174A and 174B while obtaining the effects described above.

  Further, as in this embodiment, the oil guide plate 152 can be used to actively scrape and use the lower lubricating oil in the power transmission device, so that the amount of lubricating oil to be sealed can be reduced. This makes it possible to reduce the cost of the lubricating oil and reduce the weight of the entire apparatus. Further, stirring loss during operation can be reduced, and operation efficiency can be improved. Furthermore, since less waste oil is required, the burden on the environment can be reduced.

  Subsequently, a geared motor GM610 including a power transmission device 612, which is another example of the embodiment of the present invention, will be described with reference to FIGS.

  The geared motor GM610 is configured by connecting a motor 614 serving as a drive source to a so-called sort-type swinging intermeshing type power transmission device 612.

  In addition, about the member which is the same as that of the geared motor GM110 mentioned above or similar here, the last two digits of the number attach | subject the same code | symbol, and duplication description is abbreviate | omitted.

  In the geared motor GM 610, the motor shaft 615 facing the inside of the power transmission device 612 is not directly engaged with (engaged with) the high speed shaft 632 to transmit power. A pinion 615 </ b> A is formed on the motor shaft 615 directly, and meshes with a first gear 682 provided on the distribution shaft 684. The distribution shaft 684 is a hollow shaft that penetrates the power transmission device 612 and is rotatable about the axis O7. Note that a cable or the like (not shown) is passed through the hollow portion. In addition to the first gear 682, a second gear 688 is formed on the distribution shaft 684. The second gear 688 is a spur gear 686 (only one spur gear 686 is shown in FIG. 6, but the axis O7 is shown). 3 are arranged at different positions of 120 degrees around the center), and the power can be distributed and transmitted. A high speed shaft 632 is connected to each spur gear 686. The three high-speed shafts 632 each have a hollow portion 672. Unlike the hollow portion 172 in the geared motor GM110 described above, the hollow portion 672 is not fitted with a motor shaft, and one of them is closed. Is formed. Further, a grease spot 680 which is an oil sump is provided so as to be integrated with the high-speed shaft 632 and integrated with the hollow portion 672. The grease spot 680 is filled with grease (not shown). The reduced rotation of the motor 614 can be transmitted to a counterpart machine (not shown) via the second output flange 658.

  In the geared motor GM110 described above, the high-speed shaft 132 only rotates at a fixed position, and the inner pin 642 revolves around the high-speed shaft 132. However, in the geared motor GM610, the high-speed shaft 632 rotates at a high speed, Similar to the pin 642, it revolves and transmits power. Eccentric bodies 634A and 634B are formed on the three high-speed shafts 632, respectively. Each eccentric body 634A, 634B has a load map in the circumferential direction (relative to the eccentric direction) in relation to the eccentric direction and the position of the high speed shaft 632 itself relative to the meshing position of the external gears 638A, 638B and the internal gear 641. The corresponding load is applied.

  Accordingly, oil outlets 670A and 670B are formed for each eccentric body of each high-speed shaft 632 except for a direction (contact surface) where the load from the eccentric body bearings 636A and 636B is relatively large.

  In the case of this sort-type geared motor GM610, the way of applying a load to each eccentric body is different from the case of the above-mentioned geared motor GM110 due to its structure, and accordingly, the load is a “relatively large” portion. Means a portion where 75% or more of the maximum load is applied.

  In the present embodiment, the grease spot 680 is provided on the second output flange 658 so as to be integrated with the hollow portion 672 and is filled with grease, so that the oil outlets 670A and 670B are used over a long period of time. Lubricating oil that can be supplied is present, and the frequency of maintenance (such as grease replenishment) can be reduced.

  In addition, although all the power transmission apparatuses mentioned above were the structures provided with the two external gears, it is not restricted to this, It is good also as a structure of 1 sheet or 3 sheets or more. Moreover, although all were the structure of 1 step transmission (deceleration), you may comprise in 2 steps or more. The transmission capacity can be changed as appropriate according to the usage situation. In addition, the eccentric body in the present invention includes the above-described eccentric body, but other than the above, the thin external gear is bent and shaken like a wave generator in a flexure meshing type power transmission device. The thing which produces the rotation motion accompanied by a dynamic motion is also included.

  The present invention can be applied not only to the speed reducer described as the embodiment but also to a power transmission device that uses a gear such as a speed increaser.

GM110 ... Geared motor K1 ... Transmission mechanism 112 ... Power transmission device 114 ... Motor 115 ... Motor shaft 119, 120, 146, 150 ... Bolt 122 ... Low speed shaft (output shaft)
124, 126, 128, 130 ... Bearing 132 ... High speed shaft (input shaft)
134A, 134B ... eccentric bodies 136A, 136B ... eccentric body bearings 138A, 138B ... external gears 139A, 139B ... inner pin holes 140 ... outer pins 142 ... inner pins 144 ... inner rollers 152 ... oil guide plates 160 ... oil guide holes 162 ... Return oil guide 170A, 170B ... Oil outlet 172 ... Hollow part 174A, 174B ... Contact surface 176A, 176B ... Retainer

Claims (7)

An internal gear,
An external gear that has a slight difference in the number of teeth from the internal gear and that meshes internally with the internal gear;
An eccentric body capable of swinging the external gear via a bearing,
The eccentric body has a hollow portion into which lubricating oil can flow,
An oil blowing hole penetrating from the hollow portion to a contact surface of the eccentric body with the bearing is provided. In claim 1,
The oil blower outlet is formed in a portion other than a portion of the contact surface where the load from the bearing is relatively large. In claim 1 or 2,
Furthermore, the oil outlet is formed within a range of ± 15 degrees with respect to the anti-eccentric direction of the eccentric body. In claim 1 or 2,
Furthermore, the oil outlet is formed within a range of ± 15 degrees with respect to the eccentric direction of the eccentric body. In any one of Claims 1 thru | or 4,
An output flange for taking out the reduced speed rotation generated by the meshing of the internal gear and the external gear is provided, and the output flange includes an oil guide plate for scooping up oil and the scooped up oil into the hollow portion. A power transmission device characterized in that an oil guide hole is provided. In any one of Claims 1 thru | or 5,
An oil sump is additionally provided in the hollow portion. In claim 6,
A power transmission device comprising: an output flange for taking out reduced speed rotation generated by meshing between the internal gear and the external gear, wherein the oil stop is formed on the output flange.

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