JP2006292075A - Flange-positioning structure of planetary gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a structure for simply positioning a flange in the axial direction in a reduction device of a type in which inner pins of planet gears are supported on both sides by a pair of flanges. <P>SOLUTION: The flange-positioning structure of a planetary gear comprises an external gear (planet gear) 116, a plurality of inner pins 140 passing through the external gear 116, a 1st flange 120 and a 2nd flange 130 which are placed axially on both sides of the external gear 116, and penetrated by the plurality of inner pins 140, and a connection plate 170 fastened to either one of the 1st flange 120 and the 2nd flange 130, and the plurality of the inner pins 140 by bolts 180, 182 (a 1st and a 2nd fastening means respectively). Positioning in the axial direction of the 2nd flange 130 with respect to the inner pins 140 is done through the medium of the connection plate 170 by fastening with the bolts 180, 182. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a flange positioning structure for a planetary gear device.

  A planetary gear device having a planetary gear has a penetrating pin that passes through the planetary gear and is subjected to the revolution or rotation torque of the planetary gear. The through pin takes out the revolution or rotation component of the planetary gear, or gives a reaction force so that the planetary gear does not revolve or rotate. In this specification, this penetrating pin will be referred to as an “inner pin” for convenience. An inner roller may be rotatably covered on the inner pin in order to reduce sliding resistance with the planetary gear.

  When both inner pins are supported, a configuration in which first and second flanges are arranged on both sides in the axial direction of the planetary gear and both end portions of the inner pins are inserted into the first and second flanges is often employed.

  In this case, the first and second flanges have an appropriate gap (a slight axial clearance between the members so that the rotation of the inner rollers, planetary gears, etc. existing between the first and second flanges is not hindered). It must be positioned in a state of maintaining a certain interval).

  As a configuration for positioning the first and second flanges in the axial direction, for example, Patent Document 1 discloses a method of forming a step (with different diameters) on the inner pin and positioning using the step. ing.

  Patent Document 2 also proposes a method in which a penetrating pin called a carrier pin having a function of determining the distance between the first and second flanges is separately prepared and positioned via the carrier pin. The carrier pin in this case is similar in appearance to the inner pin, but is basically non-contact with the planetary gear, and there is no direct power transmission from the planetary gear.

  In any configuration, in order to perform fine adjustment of axial positioning (specifically, for example, pressurization adjustment of bearings supporting the first and second flanges), a spacer generally referred to as “shim” is used. Is disposed between the flange and the bearing.

JP 2000-65162 A Japanese Patent Laid-Open No. 11-280854

  However, in the configuration in which the first and second flanges are positioned in the axial direction using the step formed on the inner pin, stress concentration occurs in the step due to power transmission, and this portion increases the strength. There is a problem that it becomes weak. For this reason, the inner pin needs to have a size (large diameter) that does not cause a problem in strength even when such stress concentration occurs, and in particular, increases in the radial dimension and weight.

  In addition, in the case where a carrier pin for positioning and connecting the first and second flanges is separately provided, the carrier pin does not directly extract power from the planetary gear, so the carrier pin exists. As a result, (in terms of space) the number of inner pins had to be reduced, so that the diameter of each inner pin had to be increased.

  In addition, all of the conventional configurations have an optimum shim if the bearing assembly pressure obtained when assembled using a specific shim for fine adjustment of the axial positioning is inappropriate. There is a problem that it is necessary to remove at least one of the first flange and the second flange in order to replace it. That is, when the first flange or the second flange is disassembled, all the inner pins (or carrier pins) are in a state of being fluttered, so that reassembly requires a lot of time and labor, and workability is extremely poor. There was a problem.

  The present invention has been made to solve such a conventional problem, and a planetary gear device that can realize the axial positioning of the flange with a simple and low-cost configuration by a novel coupling structure. It is an object of the present invention to provide a flange positioning structure.

  The present invention includes a planetary gear, a plurality of inner pins that penetrate the planetary gear, first and second flanges that are disposed on both sides in the axial direction of the planetary gear, and into which the plurality of inner pins are inserted, and the first A coupling plate fastened by fastening means to both one of the second flanges and the plurality of inner pins, and the inner pin of the one flange via the coupling plate by fastening by the fastening means The above-described problem is solved by the configuration in which the positioning in the axial direction is possible.

  The present invention includes a connecting plate that is connected and fixed to both the one flange and the inner pin by the fastening means. Accordingly, the inner pin and the one flange can be integrated (fixed) via the connecting plate, and the one flange can be attached (even if no stepped portion or the like is formed on the inner pin). Easy positioning with respect to the inner pin.

  Therefore, for example, if each inner pin itself can be maintained in a fixed state with respect to either the first or second flange by some other method, the inner pin is fixed with respect to either of the flanges. Thus, the remaining flanges can be positioned in the axial direction, and as a result, both flanges can be properly positioned. Moreover, since the inner pin, the connecting plate, and one of the flanges are fastened by “fastening means”, the workability of assembly, especially fine adjustment of positioning by inserting shims, etc. (with both flanges attached) It can be done very easily.

  In addition, about the structure which fixes each inner pin itself to one of flanges with a certain method, it can implement | achieve easily, without producing a technical problem in particular. For example, the inner pin may be “press-fitted / fixed” to any of the flanges, or may be fixed using a removable fixing means such as a bolt. Furthermore, “fixing by a connecting plate and fastening means” according to the present invention may be adopted for any one of the flanges. In this case, the same fastening structure is applied to both sides of the inner pin after all.

  In the present invention, the shape of the inner pin itself is not particularly limited, but the shape of the inner pin can also be a simple cylindrical shape (without a stepped portion). It is also possible to arrange an inner pin (contributing to power transmission) where the carrier pin was.

  The axial positioning of the first and second flanges can be realized with a simple and low-cost configuration.

  Hereinafter, an example of an embodiment of the present invention will be described in detail based on the drawings.

  1 and 2 show a swinging intermeshing planetary gear device to which an example of an embodiment of the present invention is applied.

  The planetary gear device 110 includes an input shaft 112, an eccentric body 114 (114A, 114B), two external gears (planetary gears) 116 (116A, 116B), and an internal gear 118. A first flange 120 and a second flange 130 are rotatably disposed on both sides in the axial direction of the external gear 116 via first and second bearings 162 and 164, and both ends of the inner pin 140 passing through the external gear 116. Each part is inserted.

  The input shaft 112 is rotatably supported by a bearing 166 and a bearing 168 incorporated in the first and second flanges 120 and 130, respectively. The input shaft 112 includes a hollow portion 112A having a large diameter at the center (hollow structure), and a bolt hole 112B for fixing a gear for receiving power from the motor side (not shown).

  Two eccentric bodies 114 are formed integrally with the input shaft 112 (114A, 114B). As shown in FIG. 2, the center Oe of the outer periphery of the eccentric body 114 </ b> A is eccentric by ΔE with respect to the axis Oi of the input shaft 112. Further, the eccentric phases of the eccentric bodies 114A and 114B are shifted from each other by 180 degrees.

  The two external gears 116A and 116B are rotatably mounted on the eccentric bodies 114A and 114B via bearings 117 (117A and 117B), respectively. The reason why the two external gears 116 are arranged in parallel in the axial direction is to increase the transmission capacity. Each external gear 116 includes inner roller holes 116 </ b> A <b> 1 and 116 </ b> B <b> 1 that pass through the external gear 116.

  An inner roller 142 is rotatably mounted on the outer periphery of the inner pin 140 to reduce sliding resistance. The inner pin 140 passes through the inner roller holes 116A1 and 116B1. The outer diameter of the inner roller 142 is smaller than the inner diameter of the inner roller holes 116A1 and 116B1 by a size corresponding to the ΔE. This is a configuration for extracting only the rotation component to the inner pin 140 while absorbing the oscillation component of the external gear 116. The inner pin 140 has a simple columnar shape without a step portion, and its end surface 140E is exposed to a recess (axial end surface) 136 of the second flange 130. The inner pin 140 is formed with a screw hole 140S extending in the axial direction from the end surface 140E (described later). In addition, the conventional carrier pin for the purpose of coupling | bonding the 1st, 2nd flanges 120 and 130 is not provided.

  The internal gear 118 is integrated with the casing 111 of the planetary gear device 110. The casing 111 is fixed to an external member. The internal teeth 118 </ b> R of the internal gear 118 are specifically configured by roller-shaped pins and can mesh with the external teeth 116 </ b> C of the external gear 116.

  The first flange 120 is rotatably supported on the casing 111 via a first bearing 162 on one axial side of the external gear 116. The first flange 120 includes a first through hole 122 into which one end of the inner pin 140 is inserted (press-fitted). As for the 1st bearing 162, the outer ring | wheel 162A contact | abuts to the projection part 111A of the casing 111, and the movement of the left direction of FIG. 1 is restrained. The first flange 120 has a stepped portion 120 </ b> A and is in contact with the inner ring 162 </ b> B of the first bearing 162.

  The second flange 130 is rotatably supported by the casing 111 via a second bearing 164 on the other axial side of the external gear 116. As for the 2nd bearing 164, the outer ring | wheel 164A contact | abuts to the projection part 111B of the casing 111, and the movement of the right direction of FIG. 1 is restrained. The second flange 130 has a stepped portion 130 </ b> A and is in contact with the inner ring 164 </ b> B of the second bearing 164. As shown in FIG. 3, the second flange 130 includes a plurality of (two in the illustrated example) two second through holes 132 at equal intervals in the circumferential direction in which the inner pins 140 are inserted (movably) with an intermediate fit. ) Prepare. The second flange 130 includes a plurality (six in the illustrated example) of screw holes 134 into which bolts (first fastening means) 180 described later are screwed between the second through holes 132. The second flange 130 has a ring-shaped recess 136 formed on the other axial side of the external gear 116.

  In addition, the code | symbol 138 of FIG. 3 is a step part which accommodates the edge part of the said inner roller 142, and the code | symbol 139 is an edge part for positioning of the external gear 116B.

  Referring to FIGS. 1 and 5, a connecting plate 170 is fitted into the ring-shaped recess 136 of the second flange 130 via a shim 176.

  As shown in FIG. 4, the connecting plate 170 is a donut-shaped flat plate as a whole, and has twelve inner pin fixing through holes 172 at positions corresponding to the second through holes 132 of the second flange 130. In addition, six second flange fixing through holes 174 are provided at positions corresponding to the screw holes 134. The shim 176 has a flat donut shape, and has through holes (not shown) at positions corresponding to the inner pin fixing through holes 172 and the second flange fixing through holes 174 of the connecting plate 170.

  Bolts (first fastening means) 180 are inserted into the connecting plate 170 through the six second flange fixing through holes 174 of the connecting plate 170 (see FIG. 1), respectively. Are screwed into the six screw holes 134. On the other hand, as shown in a partially enlarged view in FIG. 5, bolts (second fastening means) 182 are inserted into the 12 through holes 172 of the same connecting plate 170, and the bolts 182 are respectively connected to the inner pins 140. Screwed into the formed screw hole 140S. That is, the connecting plate 170 is fastened and fixed to both the second flange 130 and the inner pin 140 by the bolts 180 and 182.

  Next, the operation of the planetary gear device 110 will be described.

  When the input shaft 112 is rotated by rotation of a motor shaft (not shown), the eccentric body 114 integrated with the input shaft 112 is rotated. Since the outer periphery of the eccentric body 114 is eccentric by ΔE with respect to the axis Oi of the input shaft 112, the rotation of the eccentric body 114 causes the two external gears 116 to have a phase difference of 180 degrees via the bearing 117. Oscillates and rotates while inscribed in the internal gear 118. In this example, the internal gear 118 is integrated with the casing 111 and is fixed to an external member. Therefore, when the external gear 116 swings once by the rotation of the input shaft 112 once, the external gear 116 is equivalent to the difference in the number of teeth of the two gears 116, 118 with respect to the internal gear 118. Will rotate relatively (spin).

  This relative rotation is transmitted to the inner pin 140 through loose fitting of the inner roller holes 116A1 and 116B1 and the inner roller 142, and is further transmitted as the rotation of the first and second flanges 120 and 130. As a result, by using any one of the first and second flanges 120 and 130 as an output body, it corresponds to (the number of teeth difference between the internal gear 118 and the external gear 116) / (the number of teeth of the external gear 116). The reduction ratio to be achieved can be realized. It is also possible to fix the first and second flanges 120 and 130 and use the casing 111 itself as an output body (so-called frame rotation structure).

  Here, the operation relating to the positioning of the first and second flanges 120 and 130 and the fine adjustment thereof will be described in detail.

  The first bearing 162 is restrained from moving in the left direction in FIG. 1 by the outer ring 162 </ b> A coming into contact with the protrusion 111 </ b> A of the casing 111. A portion of the first flange 120 abuts against the inner ring 162B of the first bearing 162, so that the leftward movement in FIG. Further, since one end of the inner pin 140 is press-fitted and fixed to the first through hole 122 of the first flange 120, the leftward movement in FIG.

  Here, the connecting plate 170 is fastened to the second flange 130 by screwing the bolt 180 into the screw hole 134 of the second flange 130, while the bolt 182 is screwed into the screw hole 140 </ b> S of the inner pin 140. The inner pin 140 is fastened. Therefore, the second flange 130 is integrated with the inner pin 140 (although it slides along the second through hole 132 of the second flange 130 at the time of tightening, but eventually). Therefore, the second flange 130 is eventually incorporated in a state in which the movement is restricted both in the right direction and the left direction in the drawing, whereby the first and second flanges 120 and 130 are positioned. . The order of tightening the bolts 180 and 182 at the time of assembly is not particularly limited.

  After the tightening, the first and second flanges 120 and 130 are positioned at both ends via the inner pin 140, and the external gear 116, the inner roller 142 and the like existing therebetween are tightened in the axial direction. Therefore, the rotational properties of these members are not hindered.

  Further, by adjusting the axial thickness of the shim 176 to be inserted, the interval between the first and second flanges 120 and 130 can be slightly changed. Therefore, the first and second bearings can be adjusted by adjusting the interval. The assembly pressures 162 and 164 can be adjusted optimally.

  In other words, if a thin shim 176 is inserted, the distance between the first and second flanges 120 and 130 can be increased accordingly, so that the assembly pressure of the first and second bearings 162 and 164 can be reduced (more Can be assembled with high rotational smoothness). Conversely, if a thick shim 176 is inserted, the distance between the first and second flanges 120 and 130 is reduced accordingly, and the assembly pressure of the first and second bearings 162 and 164 can be increased (more backlash). Small assembly)

  Even when the shim 176 is replaced several times when performing this adjustment, it is only necessary to remove the connecting plate 170 by loosening the bolts 180 and 182. Therefore, the first and second flanges 120 and 130 are disassembled. There is no need. Therefore, workability can be significantly improved compared to the conventional case.

  Since the inner pin 140 is a simple cylinder and does not have a stepped portion, the cost can be reduced, and a problem that stress concentration occurs only in a part can be avoided. Therefore, durability can be sufficiently ensured even with a finer inner pin than in the prior art. As a result, not only the inner pin 140 but also the external gear 116 through which the inner pin 140 passes and the external gear 116 mesh. The internal gear 118 can also be reduced in size, and the entire apparatus can be made compact and lightweight.

  Furthermore, since it is not necessary to separately prepare carrier pins dedicated for positioning and connection, it is possible to arrange all the inner pins 140 at the locations where the conventional carrier pins existed, thereby increasing the overall transmission capacity accordingly. Is done.

  In the above embodiment, the shim 176 is interposed between the connecting plate 170 and the second flange 130. For example, as shown in FIG. 6, the end surfaces of the connecting plate 170 and the inner pin 140 are used. The same effect can be obtained even if the shim 177 is interposed between the E and 140E (however, the relationship between the thickness of the shim 177 and the level of the pressurization is opposite to the previous insertion example). .

  FIG. 7 shows an example of another embodiment of the present invention. The planetary gear device 210 employs a fixing structure using the connection plate 270D similar to that of the first embodiment for fixing the first flange 220 and the inner pin 240. As a result, this planetary gear device can perform shim adjustment of the first and second flanges 220 and 230 from both sides of the first flange 220 and the second flange 230.

  In the example of FIG. 7, the first flange 220 side of the input shaft 212 is formed thick because the bolt hole for taking in power is formed in the input shaft 212. As a result, the first and second flanges are formed. Strictly speaking, 220 and 230 do not have the same shape, but the shapes of both flanges can be made the same by design, and in that case, the cost of the flange and its positioning system can be greatly reduced. .

  Since the other configuration is basically the same as that of the previous embodiment, the same or similar parts as those of the previous embodiment are denoted by the same reference numerals in the last two digits in FIG. Only the sub code D is added to the description, and the duplicate description is omitted.

  In the above embodiment, the gap between the two flanges is adjusted by inserting a shim, and as a result, the assembly pressure of the flange bearing can be adjusted at the same time. As for the adjustment of the pressure, it is not always necessary to pair this with positioning.

  FIG. 8 shows an example. In the example of FIG. 8, the center of the first flange 320 extends in the axial direction, and a bearing 362 is disposed in the extending portion 320A. The second flange 330 is integrated with a solid output shaft 350, and a bearing 364 is disposed on the output shaft 350. The inner pin 340 is fixed to the second flange 330 side by press-fitting, and the present invention is applied to the first flange 320 side. That is, reference numeral 370 in the figure is a connecting plate, 380 is a bolt as a first fastening means, and 382 is a bolt as a second fastening means. In the case of this embodiment, the fastening of the bolts 380 and 382 does not particularly contribute to the pressure adjustment of the bearing 362 or 364. However, similarly, the first flange 320 can be positioned with a simple configuration.

  9 and 10 are application examples of the planetary gear device to which the embodiment of the present invention is applied.

  The planetary gear device 410 shown in FIG. 9 inputs the rotation of the motor M to the input shaft 412 via the pulley device P and outputs it from the second flange 430. The present invention is applied to the positioning of the first flange 420. On the other hand, the planetary gear device 510 shown in FIG. 10 shows a so-called frame rotation type application example in which the first flange 520 is fixed to the external member Ex via a bolt 513 and the internal gear 518 (casing 511) is rotated. ing. The specific configuration of each planetary gear device 410, 510 itself is the same as that already described, and therefore, the same or similar parts in the figure are given the same reference numerals in the last two digits, and are duplicated. Description is omitted.

  The planetary gear device according to the present invention can be used in various ways as described above, and the same effects can be obtained in any case.

  In a reduction gear of a type in which the inner pin of the planetary gear is supported at both ends by a pair of flanges, it can be used for positioning the flange in the axial direction.

The longitudinal cross-sectional view of the planetary gear apparatus with which the positioning structure of the flange which concerns on embodiment of this invention was applied Sectional view along the line II-II in FIG. Front view depicting the second flange as a single item and sectional view taken along the line III (B) -III (B) Front view depicting the connecting plate as a single item, and a cross-sectional side view along arrows IV (B) -IV (B) Partial enlarged sectional view showing the vicinity of the end of the inner pin Partial enlarged sectional view corresponding to FIG. 5 showing another example of shim insertion The longitudinal cross-sectional view of the planetary gear apparatus to which the positioning structure of the flange which concerns on other embodiment of this invention was applied. The longitudinal cross-sectional view of the planetary gear apparatus with which the market structure of the flange which concerns on further another embodiment of this invention was applied. Sectional drawing which shows the application example of the planetary gear apparatus with which this embodiment was applied Sectional view showing another application example

Explanation of symbols

110 ... Planetary gear device 112 ... Input shaft 114 ... Eccentric body 116 ... External gear (planetary gear)
118 ... Internal gear 120 ... First flange 122 ... First through hole 130 ... Second flange 132 ... Second through hole 134 ... Screw hole 136 ... Recess 140 ... Inner pin 162 ... First bearing 164 ... Second bearing 170 ... Connecting plate 180 ... bolt (first fastening means)
182 ... bolt (second fastening means)

Claims (7)

Planetary gears,
A plurality of inner pins penetrating the planetary gear;
First and second flanges disposed on both sides in the axial direction of the planetary gear and into which the plurality of inner pins are inserted;
A connection plate fastened by fastening means to both one of the first and second flanges and the plurality of inner pins;
A flange positioning structure for a planetary gear device, characterized in that, by fastening by the fastening means, axial positioning of the one flange with respect to the inner pin can be performed via the connecting plate. In claim 1,
Of the first and second flanges, the one flange is movable in the axial direction with respect to the plurality of inner pins,
Of the first and second flanges, the other flange is fixed to the plurality of inner pins,
The one flange is moved in the axial direction with respect to the inner pin by fastening of the fastening means, and then positioned with respect to the inner pin via the connecting plate, so that the first and second flanges are positioned. A positioning structure for a flange of a planetary gear device, characterized in that positioning in the axial direction is performed. In claim 1,
Each of the first and second flanges is movable in the axial direction with respect to the plurality of inner pins,
First and second connecting plates, which are fastened by a plurality of inner pins and fastening means, are disposed on the first and second flanges, respectively.
One of the first and second flanges is connected and positioned with respect to the inner pin by fastening of the connecting plate by the corresponding fastening means on one side,
By positioning the other flange in the axial direction with respect to the inner pin by fastening the connecting plate by the fastening means on the other side, the axial positioning between the first and second flanges is performed. A structure for positioning a flange of a planetary gear device. In any one of Claims 1-3,
A flange positioning structure for a planetary gear device, wherein the first and second flanges have the same shape. In any one of Claims 1-4,
The fastening means includes first fastening means for fastening the connecting plate and one of the first and second flanges, and second fastening means for fastening the connecting plate and the inner pin. Flange positioning structure for planetary gear unit. In claim 5,
The end face of the inner pin is exposed from the axial end face of any of the flanges,
The connecting plate is a donut-shaped plate that can be opposed to an end surface of the inner pin and an axial end surface of any one of the flanges;
The first fastening means fastens the connecting plate and the axial end surface of any one of the flanges;
The positioning structure of the flange of the planetary gear device, wherein the second fastening means is configured to fasten the same connecting plate and the end face of the inner pin. In any one of Claims 1-6,
The first and second flanges are supported by first and second bearings, respectively, between the connecting plate and the inner pin, or between the connecting plate and the first and second flanges, Shims can be placed,
The positioning structure of the flange of the planetary gear device, wherein the pressurization adjustment of the first and second bearings is possible by fastening of the fastening means.

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