JP2009047214A - Oscillation inner gearing gear reducer - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an oscillation inner gearing gear reducer reducing mechanical noise and maintaining lubrication performance of a bearing part or the like satisfactory by reducing a so called drift of grease. <P>SOLUTION: The oscillation inner gearing gear reducer 100 including external gears 126, 128, and an internal gear 136 provided with a plurality of external pins 140 at internal teeth I1, I2, ..., internally gearing with external teeth M1, V1, M2, V2, ..., of the external gears 126, 128, includes a support part 136b formed at axial direction both ends of a main body of the internal gear 136 for supporting both ends of the external pin 140, and a sound absorbing member 160 disposed between the support parts 136b and disposed in a clearance between at least part of the external pins 140 out of the plurality of the external pins 140. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a swinging internal meshing gear reducer having an external gear and an internal gear in which internal teeth internally meshing with the external teeth of the external gear are constituted by a plurality of external pins.

  Conventionally, in a swinging internal meshing gear reducer, noise is generated due to contact between an external gear and an external pin or an external roller fitted on the external pin. In order to suppress such noise, a swinging internal meshing gear reducer as shown in Patent Document 1 has been proposed. In this swinging internal meshing gear reducer, the internal teeth of the internal gear are constituted by external pins, and the external pins are covered with external rollers, and a ring-shaped vibration absorbing material such as an O-ring is provided on the outer periphery of the external rollers. By making the contact, the noise generated by the contact between the outer roller and the outer pin or the contact between the external gear and the outer roller is absorbed, thereby reducing the noise.

JP 2005-201310 A

  However, it has been newly discovered that, particularly in a swinging internal meshing gear with a low reduction ratio, a resonance effect is produced in the sound space because the distance between the outer pins is wide. For this reason, it has been difficult to sufficiently reduce noise with the swinging internal meshing gear reducer described in Patent Document 1. This is considered to be due to the fact that it did not sufficiently function as a noise reduction method against the noise generated at the time of close contact between the external gear and the outer roller.

  Note that grease may be used as a lubricant in the swinging internal meshing gear reducer. However, in the swinging internal meshing gear reducer described in Patent Document 1, the swinging internal meshing gear reducer is described. Due to the rotational centrifugal force of the rotating elements that make up the grease, grease is lost from sliding parts such as bearings that require essential lubrication, and so-called grease accumulation is generated between the outer pins and the outer pins. There is also a possibility that the lubrication performance of the bearing portion of the internal meshing gear reducer is lowered.

  The present invention has been made in order to solve the above-mentioned conventional problems, and reduces the noise of the oscillating internal meshing gear reducer, and further reduces the so-called grease accumulation and improves the lubrication performance of the bearing portion and the like. It is an object of the present invention to provide a swinging internal meshing gear reducer that maintains a good condition.

  The present invention provides a swinging internal meshing gear reducer having an external gear and an internal gear in which internal teeth internally meshing with the external teeth of the external gear are constituted by a plurality of external pins. A support portion formed at both ends in the axial direction of the main body of the internal gear for supporting both ends of the outer pin, and disposed between the support portions, and at least a portion of the plurality of outer pins between the outer pins The above-mentioned problem is solved by having a sound absorbing member disposed in the gap between them.

  According to the present invention, since the sound absorbing member is disposed in the gap between at least some of the plurality of outer pins, the inner gap of the swinging internal meshing gear reducer is narrowed. That is, since the internal gap is narrowed, the acoustic resonance effect that can amplify the generated noise is reduced, and the sound absorbing member exists in the space and can absorb the acoustic energy.

  In addition, a sound absorbing member that fills a gap between at least some of the plurality of outer pins between the support portions formed at both ends in the axial direction of the main body of the internal gear in order to support both ends of the outer pin. Therefore, even if the rotational centrifugal force of the rotating elements that make up the oscillating internal meshing gear reducer works, the grease is not physically present in the gap between the outer pins where the grease has been sprayed. Therefore, grease can always be supplied to the outer pin and the bearing portion of the outer roller without excessively injecting grease.

  Note that it is not always necessary for the sound absorbing member to fill all the gaps between the plurality of outer pins, and a corresponding effect can be obtained even with only a part of the sound absorbing member. In some cases, it is preferable that the sound absorbing member be disposed without contacting the outer pin itself (described later).

  According to the present invention, it is possible to reduce noise by reducing the internal gap of the swinging internal meshing gear reducer. In addition, since the lubrication performance of the bearing portion can be improved, it is possible to prevent a decrease in the lubrication performance of the bearing portion. At the same time, it is possible to reduce the consumption amount of grease which has been a conventional spray pool.

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

  1 is a side sectional view of an intermeshing planetary gear reducer according to the present embodiment, FIG. 2 is a sectional view taken along line II-II in FIG. 1, and FIG. 3 is an enlarged view of a broken line region in FIG. 4 is a cross-sectional view taken along line IV-IV in FIG.

  First, the configuration of the intermeshing planetary gear reducer according to the present embodiment will be described with reference to FIGS. The intermeshing planetary gear speed reducer 100 includes eccentric bodies 110 and 112 integrated with the input shaft 102 and external gears 126 and 128 that swing and rotate by the eccentric bodies 110 and 112. Further, the internally meshing planetary gear reducer 100 includes an internal gear 136 in which internal teeth that internally mesh with external teeth of the external gears 126 and 128 are constituted by a plurality of external pins 140, and the internal gear 136. The sound absorbing member 160 fitted in the groove 136a between the support portions 136b formed at both ends in the axial direction of the main body of the main body, and the rotation components of the external gears 126, 128 disposed on the outer side in the axial direction of the external gears 126, 128 And a flange body 152 connected to an inner pin 148 for taking out the. Hereinafter, each component will be described in detail.

  The input shaft 102 is supported by a pair of bearings 104 and 106 as shown in FIG. The bearing 104 is supported by the input stage cover 144. The bearing 106 is supported by an inner surface of a flange body 152 that is integral with the output shaft 154. The eccentric bodies 110 and 112 have an eccentric phase shifted by 180 degrees, respectively, and the amount of eccentricity is e1 (FIG. 2). Roller bearings 114 and 120 are arranged between the external gears 126 and 128 outside the eccentric bodies 110 and 112.

  As shown in FIG. 1, the external gears 126 and 128 are fitted on the outer periphery of the eccentric bodies 110 and 112 via roller bearings 114 and 120, and the outer diameter (tooth tip circle diameter) is r2 (FIG. 2). It is. The external gears 126 and 128 respectively have a plurality of inner pin holes 130 and 132 penetrating in the axial direction, and the inner roller 150 is loosely fitted in the inner pin holes 130 and 132. In other words, the external gears 126 and 128 are oscillated and rotated by the rotation of the eccentric bodies 110 and 112, and are internally meshed with the internal gear 136. In the present embodiment, the external gears 126 and 128 have the same shape, and the number of teeth of the internal gear 136 is 14, so that the number of teeth is 12, which is two less. The reason why the two external gears 126 and 128 are arranged is to secure the power transmission capacity. The spacer 134 is inserted between the external gear 126 and the external gear 128 so that the interval is constant.

  The main body of the internal gear 136 is integrated with the casing 142 as shown in FIG. The plurality of outer pins 140 and the outer roller 138 fitted on the outer periphery of the outer pin 140 constitute inner teeth, which are in mesh with the outer teeth of the external gears 126 and 128. In order to support both ends of the outer pin 140, support portions 136b are formed at both ends in the axial direction of the main body of the internal gear 136. A groove 136a is provided between the support portions 136b. As shown in FIG. 2, a sound absorbing member 160 is fitted in the groove 136a.

  As shown in FIG. 2, the sound absorbing member 160 has an annular shape, and includes a metal plate 162 in contact with the bottom surface of the groove 136a on the outer periphery, and a plurality of convex portions 164 made of resin on the inside. ing. That is, the sound absorbing member 160 is outside the outer pin 140 and is fitted into the groove 136a, and the convex portion 164 is a space between the outer pin 140 and the outer pin 140 (between the outer pins 140). Arranged to fill part. That is, the sound absorbing member 160 is disposed so as to fill a part of the gap between the outer pins 140. If these relations are shown in FIG. 2, a circle having a radius R1 in contact with the outer periphery of the outer pin 140 on the input shaft 102 side from the center of the input shaft 102, and an outer periphery of the outer pin 140 on the casing 142 side from the center of the input shaft 102. A distance R2 from the center of the input shaft 102 to the inner surface of the sound absorbing member 160, that is, the surface of the convex portion 164 exists in an annular region formed by the circle having the radius r1 (formula (1) )).

          R1 ≦ R2 ≦ r1 (1)

  In this embodiment, the said metal plate 162 is stainless steel (SUS304 etc.), for example, and thickness t1 is 0.2-0.3 mm. If the thickness t1 of the metal plate 162 is too thick, the sound absorbing member 160 becomes too rigid and it is difficult to fit the sound absorbing member 160 into the groove 136a. In the portion where the outer diameter of the outer pin 140 is closest to the bottom surface of the groove portion 136a of the main body of the internal gear 136, only the metal plate 162 of the sound absorbing member 160 is disposed in the groove portion 136a of the main body of the internal gear 136. Specifically, as shown in FIG. 3, the distance T from the outer peripheral surface of the outer roller 138 to the bottom surface of the groove 136a is about 0.5 mm, and the thickness t1 of the metal plate 162 is 0.2 to 0.3 mm. Therefore, since the metal plate 162 does not contact the outer roller 138 fitted to the outer pin 140, the metal plate 162 facilitates the arrangement of the sound absorbing member 160 without hindering the rotation of the outer roller 138.

  The convex portion 164 is made of a resin, for example, a silicon resin that easily elastically deforms, absorbs shock and vibration when the external gears 126 and 128 are in contact, and has high oil resistance. As shown in FIG. 2, the convex portion 164 is a substantially rounded rectangular parallelepiped, and is spread and joined at a gentle skirt in the vicinity of the joint with the metal plate 162. As shown in FIG. 4, the sound absorbing member 160 having the convex portion 164 substantially fills the groove 136 a in a portion where the outer pin 140 does not exist, and has a thickness that allows contact with the external gears 126 and 128. That is, as shown in FIG. 2, when the eccentric body 110 rotates with the eccentric amount e1, the rotation of the input shaft 102 in the eccentric direction (the direction indicating the maximum eccentric amount e1) as shown in the equation (2). The distance R2 from the center to the surface of the convex portion 164 is smaller than the sum of the eccentricity e1 and the outer diameter r2 of the external gear 126.

          R2 <r2 + e1 (2)

  The convex portion 164 and the metal plate 162 are joined by directly solidifying the silicon resin on the cleaned metal 162, thereby realizing a high adhesion.

  As shown in FIG. 1, the flange body 152 is disposed on the outer side in the axial direction of the external gear 128, and an inner pin 148 is connected and fixed thereto. A pipe-shaped inner roller 150 is fitted on the outer periphery of the inner pin 148 and is loosely fitted in the inner pin holes 130 and 132 of the external gears 126 and 128. Therefore, the internal pin 148 can extract the rotation components of the external gears 126 and 128 and the internal gear 136. The output shaft 154 is integral with the flange body 152 and is supported by the output stage cover 146 via a pair of bearings 156 and 158. The intermeshing planetary gear reducer 100 has grease inside as a lubricant and is sealed with oil seals 166 and 168.

  Next, the operation of this embodiment will be described with reference to FIGS.

  Power is transmitted from a power source (not shown) via the input shaft 102, and the eccentric bodies 110 and 112 attached and fixed to the input shaft 102 rotate eccentrically. Then, the external gears 126 and 128 fitted through the roller bearings 114 and 120 on the outer circumferences of the eccentric bodies 110 and 112 swing and rotate. 2, when the eccentric direction of the eccentric body 110 faces the direction of the external tooth M1 of the external gear 126, the sum of the radius r2 and the eccentric amount e1 of the external gear 126 is the convex portion 164. It becomes longer than the distance R2 to the surface of (Formula (2)). For this reason, the external teeth M1 of the external gear 126 come into contact with A1 of the convex portion 164 and elastically deform A1. Then, when the eccentric body 110 rotates in the direction of the arrow in FIG. 2, the eccentric direction is next directed toward the tooth bottom V1 of the external gear 126, and the internal teeth of the internal gear 136 at the tooth bottom V1 of the external gear 126. I1 meshes with I1 (state shown in FIG. 2). That is, after the external tooth M1 of the external gear 126 elastically deforms A1 of the convex portion 164, the adjacent internal tooth I1 and the tooth bottom V1 of the external gear 126 mesh.

  That is, as shown in FIG. 2, when the angle of the eccentric amount e1 of the eccentric body 110 shifts in order as the input shaft 102 rotates in the direction of the arrow, when the tooth bottom V2 and the internal tooth I2 mesh, A2 becomes When the tooth bottom V3 and the internal tooth I3 are engaged, A3 performs buffering at the time of meshing, and when the tooth bottom V4 and the internal tooth I4 mesh, A4 performs buffering. The same applies to the case where the input shaft 102 rotates in the reverse direction. When the root V4 meshes with the internal tooth I4, A5 is when the tooth base V3 meshes with the internal tooth I3. When the tooth bottom V2 and the internal tooth I2 mesh with each other, A3 sequentially performs buffering when meshing. At this time, even if rotational centrifugal force acts on the eccentric bodies 110 and 112, the roller bearings 114 and 120, the inner roller 150, the outer roller 138, and the external gears 126 and 128, which are rotating elements, due to the rotation of the input shaft 102. In addition, since the sound absorbing member 160 is disposed in the gap between the outer pins 140 where the grease has been blown up in the past, no grease physically exists in that portion. Further, since the outer roller 138 is not in contact with the sound absorbing member 160 at the time of internal meshing, unnecessary frictional force due to contact does not occur, and the outer roller 138 rotates smoothly around the outer pin 140.

  In this way, the external gears 126 and 128 are internally meshed with the internal gear 136 that is integral with the casing 142. Therefore, the rotation of the external gears 126 and 128 is restricted, and only the oscillation is performed. Become. However, since the swinging components of the external gears 126 and 128 are absorbed by the loose fit of the inner pins 148 and the inner rollers 150 in the inner pin holes 130 and 132, only the rotation components of the external gears 126 and 128 are extracted. Yes. At this time, the number of teeth of the external gears 126 and 128 and the number of teeth of the internal gear 136 are configured so as to have a difference of two, so when the eccentric bodies 110 and 112 make one rotation, The tooth gears 126 and 128 rotate by the difference between the two teeth. This rotation component is taken out to the flange body 152 through the inner pin 148 and the inner roller 150 loosely fitted in the inner pin holes 130 and 132.

  That is, the rotation of the input shaft 102 is reduced to (the difference in the number of teeth between the external gear 126 (= 128) and the internal gear 136) / (the number of teeth of the external gear 126 (= 128)). . In this embodiment, the difference in the number of teeth between the external gear 126 (= 128) and the internal gear 136 is 2, and the number of teeth of the external gear 126 (= 128) is 12, so the reduction ratio is 1/6. Become. The reduced-speed rotation of the flange body 152 is transmitted to the output shaft 154 formed integrally with the flange body 152, and power is transmitted to a load (not shown) with high efficiency.

  Accordingly, since the sound absorbing member 160 is disposed in the gap between the outer pins 140, the swinging internal meshing gear reducer 100 with a wide reduction ratio of 1/6 between the outer pins 140 constituting the internal gear 136 is provided. Even so, the internal gap around the outer pin 140 is narrowed. That is, since the internal space is narrowed, the acoustic resonance effect that can amplify the generated noise is reduced, and the sound absorbing member 160 is present in the space and can absorb acoustic energy, thereby reducing noise. It is possible.

  Further, a sound absorbing member that fills at least part of the gaps between the plurality of outer pins 140 between the support portions 136b formed at both ends in the axial direction of the main body of the internal gear 136 that supports both ends of the outer pins 140. 160 is arranged. For this reason, the input shaft 102, the eccentric bodies 110, 112, the roller bearings 114, 120, the inner roller 150, the outer roller 138, and the external gear 126, which are rotating elements constituting the swinging internal meshing gear reducer 100, Even if a rotational centrifugal force is applied to 128, grease cannot physically exist in the gap between the outer pins 140 where the grease has been accumulated in the past. Even if not, grease can always be supplied to the bearing portion of the outer pin 140 and the outer roller 138. That is, it is possible to prevent a decrease in the lubrication performance of the bearing portion of the oscillating internal meshing gear reducer 100, and it is possible to maintain and improve the effects of high-efficiency power transmission, long life, and noise reduction. . At the same time, it is possible to reduce the consumption of grease, which has been a conventional puddle.

  Furthermore, since the sound absorbing member 160 has a convex portion 164 having a thickness that can come into contact with the external gears 126, 128, when the external gears 126, 128 and the outer roller 138 come into contact, the external gear 126, Since the convex shape portion 164 is elastically deformed when 128 comes into contact with the convex shape portion 164 of the sound absorbing member 160, it is possible to buffer the contact close to the impact between the external gears 126, 128 and the outer roller 138. By the buffering, noise generated by the external gears 126 and 128 and the outer roller 138 can be reduced.

  Further, since the sound absorbing member 160 is inserted so as not to contact the outer roller 138, the positioning is not required to be highly accurate when it is inserted into the groove 136a of the sound absorbing member 160, and the mounting is easy. Further, by not contacting, the outer roller 138 can easily slide with respect to the outer pin 140, and unnecessary power transmission loss can be prevented when the external gears 126, 128 and the internal gear 136 are in mesh. Can do.

  Further, since the thickness t1 of the metal plate 162 is 0.2 mm to 0.3 mm, the sound absorbing member 160 is not too rigid and can be deformed, and the internal gear 136 can be easily inserted into the groove 136a. Can be done.

  The present embodiment is not limited to the intermeshing planetary gear reducer 100 having a reduction ratio of 1/6, but is inscribed with a reduction ratio of 1/50 or less where the gap between the outer pins 140 is wide. The mesh planetary gear reducer 100 is particularly effective. Further, the present invention is applicable even if the inner mesh planetary gear speed reducer 100 does not use the outer roller 138. Further, the present invention is applied even if the intermeshing planetary gear speed reducer 100 does not have the groove 136a. Even in that case, it is possible to arrange the convex portion 164 in the gap between the outer pins 140, and the corresponding effects of the present invention are exhibited.

  Further, the sound absorbing member 160 is not limited to the case where it does not contact the outer pin 140. This is because, when the sound absorbing member 160 is in contact with the outer pin 140, the vibration of the outer pin 140 can be suppressed, which is more effective in reducing noise, which is an object of the present invention.

  Further, the convex portion 164 is not limited to the case where it is arranged in the gap between all the outer pins 140, and the present invention can be applied to a part between a plurality of outer pins 140. Is possible. This is because even if it is a part, the effect of the present invention is exhibited by narrowing the grease accumulation in the part and the sound resonance space.

  Even when a silicon resin is used as the resin, the silicon resin may be bonded to the convex portion 164 with an adhesive after being molded. In this case, it is easier to form the convex portion 164. Further, the resin is not limited to the case where the entire convex portion 164 is formed, and may be a part of the surface facing the external gears 126 and 128. This is because the acoustic energy can be absorbed as long as the resin exists. Further, the resin is not limited to the silicon resin, but may be other resin or rubber, particularly fluorine rubber, nitrile rubber, or the like, or may be layered in combination with other resin. This is because it is excellent not only in oil resistance but also in wear resistance.

  The metal plate 162 is not limited to stainless steel, and an aluminum plate, a nickel plate, or the like may be used.

Side sectional view of the intermeshing planetary gear reducer 100 according to the present embodiment. Sectional view along the line II-II in FIG. Enlarged view of broken line area in FIG. Sectional view along line IV-IV in Fig. 2

Explanation of symbols

DESCRIPTION OF SYMBOLS 100 ... Internal mesh planetary gear reducer 102 ... Input shaft 104, 106, 156, 158 ... Bearing 110, 112 ... Eccentric body 114, 120 ... Roller bearing 126, 128 ... External gear 130, 132 ... Inner pin hole 134 ... Spacer 136 ... Internal gear 136a ... Groove part 136b ... Support part 138 ... Outer roller 140 ... Outer pin 142 ... Casing 144 ... Input stage cover 146 ... Output stage cover 148 ... Inner pin 150 ... Inner roller 152 ... Flange body 160 ... Sound absorbing member 162 ... Metal plate 164 ... Convex-shaped part 166, 168 ... Oil seal

Claims (4)

In a swinging internal meshing gear reducer having an external gear and an internal gear in which the internal teeth internally meshing with the external teeth of the external gear are constituted by a plurality of external pins,
Support portions formed at both axial ends of the body of the internal gear to support both ends of the outer pin;
And a sound absorbing member disposed between the support portions and disposed in a gap between at least some of the plurality of outer pins. Machine. In claim 1,
The sound-absorbing member is arranged without contacting the outer pin. In claim 1 or 2,
The sound-absorbing member has a convex-shaped portion having a thickness that can come into contact with the external gear, and is elastically deformed by the contact of the external gear. In any one of Claims 1 thru | or 3,
The sound absorbing member is characterized in that at least a part of a surface facing the external gear is covered with a resin, and is integrally held by a metal plate contacting the bottom surface of the groove. Swing internal meshing gear reducer.

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