JP2012007637A - Eccentric rocking type reduction gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To spread grease easily all over the inside of a reduction gear.SOLUTION: An eccentric rocking type reduction gear 100 includes eccentrically rocking external gears 116, 118 and 120, internal gear 130 which has internal teeth having a number of teeth slightly smaller than that of the external gears 116, 118 and 120 and is inscribingly engaged with the external gears 116, 118 and 120, and a flange 134 arranged axially sideways of the external gears 116, 118, and 120, in which at least one of a grease supply port 144 and a grease discharge port 146 is formed to the flange 134, and through-holes 152A, 154A, 154B, and 154C through which constituent members of the reduction gear 100 are not passed are formed to the external gear 116, 118, and 120 such that the holes pass through the external gears 116, 118, and 120 in the axial direction.

Description

  The present invention relates to an eccentric oscillating speed reducer.

  Patent Document 1 discloses an eccentric rocking type speed reducer 1 as shown in FIG.

  The eccentric oscillating speed reducer 1 includes an external gear 2 that oscillates eccentrically and an internal gear 3 that is in mesh with the external gear 2. The internal teeth 3A of the internal gear 3 have a slight difference in the number of teeth from the external teeth 2A of the external gear 2. Further, a flange 4 is disposed on the axial side portion of the external gear 2, and a grease supply port 5 for supplying grease to the inside of the speed reducer 1 is formed in the flange 4.

Japanese Patent Laying-Open No. 2009-204156 (FIG. 1)

  When new grease is sealed in the reducer 1 or when old grease sealed in the reducer 1 is replaced with new grease, new grease is supplied to the reducer 1 from the greasing port 5. Is done.

  In order for new grease supplied from the greasing port 5 to the inside of the reduction gear 1 to reach every corner of the reduction gear 1, the gap between the external gear 2 and the internal gear 3, the inner pin 6 and the internal gear is mainly used. It was necessary to pass through a slight gap such as the gap of the pin hole 7 or the gap of the eccentric body 8 or 9.

  However, since these gaps are very narrow, it was difficult for grease to pass through these gaps. As a result, for example, when new grease is newly enclosed in the reduction gear 1, the grease has a problem that it is difficult to spread to every corner of the reduction gear 1. In addition, when replacing the old grease enclosed in the reducer 1 with new grease, it is difficult to discharge all the old grease from the reducer 1, and as a result, replacement with new grease is sufficient. There was a fear that it was not done.

  In the present invention, in order to solve the above-mentioned problem, it is an object to be able to easily spread grease inside the reduction gear.

  The present invention includes an externally oscillating external gear, an internal gear having a slight difference in the number of teeth from the external gear of the external gear, and the internal gear with which the external gear meshes internally, In an eccentric oscillating type speed reducer provided with a flange disposed on an axial side portion of the external gear, a grease supply port for supplying grease to be sealed inside the speed reducer to the flange; At least one of the oil discharge ports for discharging the grease is formed, and a through hole through which the component of the speed reducer is not inserted is formed through the external gear in the axial direction. The above-described problem has been solved by the construction.

  In the present invention, at least one of a greasing port or a greasing port is formed in the flange, and a through hole through which a component of the speed reducer is not inserted is formed through the external gear in the axial direction. For this reason, the grease supplied from the greasing port can be smoothly moved in the axial direction of the external gear by passing through a through-hole through which no member is inserted only by applying a small sealing pressure. As a result, this grease can be easily distributed throughout the reduction gear.

  According to the present invention, grease can be easily distributed inside the reduction gear.

The longitudinal cross-sectional view of the eccentric rocking | fluctuation type reduction gear concerning embodiment of this invention The front view which shows the position of the supply and drainage port in the eccentric rocking | fluctuation type reduction gear shown in FIG. FIG. 1 is a rear view of the first flange body provided in the eccentric oscillation type speed reducer shown in FIG. 1 as viewed from the internal gear side, and a sectional view taken along the line IIIB-IIIB. Sectional view along the arrow IV-IV line of the eccentric rocking speed reducer shown in FIG. Front view of an eccentric oscillating speed reducer according to a second embodiment of the present invention. The front view and longitudinal cross-sectional view of the eccentric rocking | fluctuation type reduction gear concerning the 3rd Embodiment of this invention Longitudinal sectional view of an eccentric oscillating speed reducer according to the fourth and fifth embodiments of the present invention Front view, rear view, and longitudinal sectional view of an eccentric oscillating speed reducer according to a sixth embodiment of the present invention The front view and longitudinal cross-sectional view of the eccentric rocking | swiveling type reduction gear concerning the 7th Embodiment of this invention Longitudinal sectional view of an eccentric oscillating speed reducer showing a conventional example

  Hereinafter, an eccentric oscillating speed reducer 100 according to an example of an embodiment of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a longitudinal sectional view of an eccentric oscillating speed reducer 100. FIG. 2 is a front view showing the positions of the supply and drain ports 144 and 146 in the speed reducer 100 shown in FIG. 3 is a rear view of the first flange body 134 provided in the speed reducer 100 shown in FIG. 1 as viewed from the first external gear 116 side (FIG. 3A), and a first view shown in FIG. It is sectional drawing (FIG. 3 (B)) which follows the arrow IIIB-IIIB line | wire of 1 flange body 134. FIG. 4 is a cross-sectional view taken along line IV-IV of the speed reducer 100 shown in FIG.

  First, the overall configuration of the eccentric oscillating speed reducer 100 will be described.

  The eccentric oscillating speed reducer 100 includes first to third external gears 116, 118, 120, an internal gear 130, and first and second flange bodies 134, 136.

  First to third eccentric bodies 104, 106, and 108 are integrally formed on the outer periphery of the input shaft (hollow shaft) 102 of the speed reducer 100, and the outer periphery of the first to third eccentric bodies 104, 106, and 108 is formed. The first to third external gears 116, 118, and 120 that are eccentrically oscillated are incorporated through the first to third rollers 110, 112, and 114. Since the first to third external gears 116, 118, and 120 have the same configuration, only the first external gear 116 will be described (see FIG. 4). In the present embodiment, a plurality of six first to sixth inner pin holes 122A, 123A, 124A, 125A, 126A, 127A are formed on the same circumference with a circumferential phase difference of 60 ° intervals. ing. Six inner pins 170, 171, 172, 173, 174, and 175 described later are loosely fitted in the first to sixth inner pin holes 122A to 127A, respectively. Specific configurations of the first to third external gears 116, 118, and 120 will be described in detail later. The eccentric phases of the eccentric bodies 104, 106, and 108 are shifted by 120 °, and the eccentric phase differences of the first to third external gears 116, 118, and 120 are 120 °.

  The internal gear 130 is integrated with the inner periphery of the casing 132. The casing 132 is fixed to an external member (not shown). The internal teeth of the internal gear 130 are constituted by a plurality of cylindrical outer pins 131. The internal gear 130 has internal teeth slightly different from the external teeth of the first to third external gears 116, 118, 120, and the first to third external gears 116, 118 are included. , 120 are inscribed in mesh. Specifically, the number of external teeth of the first to third external gears 116, 118, 120 is “119”. On the other hand, on the main body side of the internal gear 130 (the part integrated with the inner periphery of the casing 132), the number of teeth is set to 120 at the position of “every other” corresponding to the number of teeth. A total of 60 outer pins 131 having a corresponding size are incorporated. In such a configuration, the substantial number of internal teeth of the internal gear 130 is the number of external pins 131 × 2 = 120. That is, the number of teeth of the internal gear 130 is “120” in this example, and the number of teeth of the internal gear 130 is “the number of teeth of the first to third external gears 116, 118, 120”. Only 1 ”(a slight difference in the number of teeth) is set.

  The first flange body 134 is disposed on the axial side portion of the first external gear 116. The second flange body 136 is disposed on the axial direction side portion of the third external gear 120. In the present embodiment, the first flange body 134 corresponds to the “flange” of the present invention. Six inner pins 170 to 175 are integrally formed on the first flange body 134. The inner pins 170 to 175 are inner pin holes 122A to 127A, 122B, and 122C of the first to third external gears 116, 118, and 120 (about other inner pin holes of the second and third external gears 118 and 120). Is not shown) in the axial direction, and is connected and fixed to the second flange body 136 by a bolt 140. The first and second flange bodies 134, 136 are synchronized with the rotation components of the first to third external gears 116, 118, 120.

  Here, “the first and second flange bodies 134 and 136 are synchronized with the rotation components of the first to third external gears 116, 118 and 120” means that the first and second flange bodies 134, 136 means that it is configured to rotate or stop together with the first to third external gears 116, 118, and 120. Specifically, as in this embodiment, when the internal gear 130 (casing 132) is fixed, the first and second flange bodies 134 and 136 have the first to third external gears 116, respectively. , 118, 120 and the first external gears 116, 118, 120, and the rotation is transmitted to the counterpart machine in synchronization with the rotation components of the first, second, and third external gears 116, 118, 120. On the other hand, when the rotation of the first to third external gears 116, 118, 120 is restricted (only swinging), and the internal gear 130 (casing 132) rotates to transmit the rotation to the counterpart machine. The first and second flange bodies 134, 136 maintain a stopped state in synchronization with the rotation components of the first to third external gears 116, 118, 120 at this time (rotation is restricted). (Fixed to the external member).

  On the outer periphery of the inner pins 170 to 175, the sliding resistance between the inner pins 170 to 175 and the inner pin holes 122A to 127A, 122B, and 122C of the first to third external gears 116, 118, and 120 is reduced. Inner rollers 180 to 185 are attached. The first and second flange bodies 134 and 136 are rotatable relative to the input shaft 102 and the casing 132. A specific configuration of the first and second flange bodies 134 and 136 will be described in detail later.

  In this reducer 100, the sliding resistance of the components of the reducer 100 (for example, between the first to third rollers 110, 112, 114 and the first to third eccentric bodies 104, 106, 108) is reduced. Grease for sealing is enclosed. In the present embodiment, the grease enclosed in the speed reducer 100 is a hard grease having a consistency number of 1 or more.

  Below, the detailed structure of the 1st flange body 134 and the 1st-3rd external gears 116, 118, and 120 is demonstrated.

  First, the first flange body 134 will be described in detail.

  Both the greasing port 144 for supplying the grease sealed inside the reduction gear 100 to the first flange body 134 and the greasing port 146 for discharging the grease penetrate the first flange body 134 in the axial direction. Is formed. In the present embodiment, the axial vertical cross sections (in the axial direction of the speed reducer 100) of the supply and drain ports 144 and 146 are both circular. The circumferential phase difference X between the centers of the greasing port 144 and the draining port 146 is 180 ° with the axis of the first flange body 134 as the center.

  Both the supply and drain ports 144 and 146 are provided with stoppers (not shown) for preventing the grease from flowing out to the external space 150. The operator removes this plug from both the supply and drainage ports 144 and 146 at the initial filling and replacement of the grease, and supplies new grease.

  Next, the first to third external gears 116, 118, and 120 will be described in detail.

  A plurality of through holes are formed in the first external gear 116. In the present embodiment, two first and second through holes 152 </ b> A and 154 </ b> A are formed on the side surface in the axial direction of the first external gear 116. The first and second through holes 152A and 154A are holes through which the constituent members of the speed reducer 100 (for example, the inner pins 170 to 175 described above) are not inserted.

  The opening area S1 of the first through hole 152A is larger than the opening area A1 of the greasing port 144. Further, the opening area S2 of the second through hole 154A is also larger than the opening area A2 of the drainage port 146. In the present embodiment, the cross sections perpendicular to the axes (in the axial direction of the speed reducer 100) of the first and second through holes 152A and 154A are circular with the same diameter. The first and second through holes 152A and 154A are formed on the same circumference as the first to sixth inner pin holes 122A to 127A. Specifically, the first through hole 152A is formed between the first inner pin hole 122A and the second inner pin hole 123A. The second through hole 154A is formed between the fourth inner pin hole 125A and the fifth inner pin hole 126A.

  152 A of 1st through-holes are formed in the position which overlaps with the greasing port 144 formed in the 1st flange body 134 at the axial view. 154A of 2nd through-holes are formed in the position which overlaps with the fat drain opening 146 formed in the 1st flange body 134 by axial direction view. That is, the circumferential phase difference Y between the centers of the first and second through holes 152A, 154A is also (as in the circumferential phase difference X between the centers of the greasing port 144 and the draining port 146, ) 180 ° centered on the axis of the first flange body 134.

  The second and third external gears 118 and 120 have the same structure as the first external gear 116. A third through hole (not shown) and a fourth through hole 154B are formed in the second external gear 118, and a fifth through hole (not shown) and a sixth through hole 154C are formed in the third external gear 120. Has been. The first through hole 152 </ b> A and the third and fifth through holes formed in the first to third external gears 116, 118, and 120 are holes larger than the opening area A <b> 1 of the greasing port 144. For this reason, even if the 1st-3rd external gears 116, 118, and 120 rotate by the amount of eccentricity, respectively, the 1st through-hole 152A and the 3rd and 5th through-holes have overlapped in the direction of an axis. In addition, the second, fourth, and sixth through holes 154A, 154B, and 154C overlap with each other when viewed in the axial direction. That is, the first through hole 152A, and the third and fifth through holes are formed at positions that overlap with the greasing port 144 when viewed in the axial direction. In addition, the second, fourth, and sixth through holes 154A, 154B, and 154C are formed at positions that overlap the fat drain port 146 when viewed in the axial direction. As a result, the supplied new grease can linearly pass through the first through hole 152A and the third and fifth through holes of the first to third external gears 116, 118, and 120 in the axial direction. It is.

  Next, the operation of the eccentric oscillating speed reducer 100 will be described.

  First, the power transmission action of the speed reducer 100 will be described.

  When rotation of a motor (not shown) is transmitted to the input shaft 102 and the input shaft 102 rotates, the first to third external gears 116, 118, and 120 swing, and the first to third external gears 116, 118 are swung. , 120 and the internal gear 130 are sequentially shifted depending on the difference in the number of teeth. In the present embodiment, since the internal gear 130 of the speed reducer 100 is fixed to the casing 132, the first to third external gears 116, 118, 120 rotate relative to the internal gear 130. (Rotates in the direction opposite to the rotation of the input shaft 102). The relative rotation (rotation) of the first to third external gears 116, 118, 120 with respect to the internal gear 130 is transmitted to the first flange body 134 via the inner pins 170 to 175, and from the first flange body 134. Is output.

  Next, the operation centering on the first flange body 134 and the first to third external gears 116, 118, 120 at the time of initial filling or replacement of grease will be described.

  Since the speed reducer 100 according to the present embodiment is an eccentric oscillating type speed reducer, the difference in the number of teeth between the first to third external gears 116, 118, 120 and the internal gear 130 is set to be small. The gaps between the first to third external gears 116, 118, 120 and the internal gear 130 are very narrow. Further, when used for precision control of industrial robots, machine tools, etc., the backlash is set to be small, and functionally, the inner rollers 180 to 185 and the first to sixth inner pin holes 122A to 127A The gap between them is only an amount corresponding to the amount of eccentricity and is extremely narrow. For this reason, the grease has a structure that is difficult to move in the axial direction within the reduction gear 100. In particular, when a grease with a high consistency number (hardness) (for example, consistency number 1 or higher) is employed as the grease enclosed in the speed reducer 100, the grease itself is decelerated while flexibly deforming its shape. It is more difficult to move the machine 100. On the other hand, when a grease having a small consistency number (softness) (for example, consistency numbers 0, 00, etc.) is employed, the inside of the reduction gear 100 can be moved more flexibly. It tends to leak easily.

  However, according to the present embodiment, the greasing port 144 is formed through the first flange body 134 in the axial direction, and the first through hole 152A, and the third and fifth through holes are respectively The first to third external gears 116, 118, 120 are formed so as to penetrate in the axial direction. In addition, the first through hole 152A, the third and fifth through holes are formed at positions overlapping the greasing port 144 when viewed in the axial direction, and are larger than the opening area A1 of the greasing port 144. . As a result, even when the grease has a large (hard) consistency number (concentration number 1 or higher) in the initial sealing operation or replacement operation of the grease, the grease passes through the first penetration only by applying a small sealing pressure. The hole 152A and the third and fifth through holes can be linearly passed in the axial direction and smoothly moved in the axial direction of the speed reducer 100. Thereby, the grease can easily reach the space between the second flange body 136 and the third external gear 120. After the grease has been filled up to this point, the grease path is changed in the radial axis direction. However, due to the magnitude of the resistance, the rear side tends to be the rear side (anti-grease port side of the third external gear 120). It will be filled from. In this way, the space between the second external gear 118 and the first external gear 116 and the space between the first flange body 134 and the first external gear 116 are sealed in this order from the counter greasing port side. In the case of a grease replacement operation, the old grease passes through the sixth, fourth, and second through holes 154C, 154B, and 154A of the third to first external gears 120, 118, and 116, It moves toward the fat removal port 146 of the flange body 134. When a part of the new grease encapsulated eventually is discharged from the oil discharge port 146, this time becomes a standard for completing the enclosing of the new grease (or completing the replacement of the old and new grease).

  Each of the first to third external gears 116, 118, 120 has a plurality of through holes (for example, the first external gear 116 has the first and second through holes 152A, 154A), the grease on the supply side and the discharge side pass through different through-holes, and the grease easily moves smoothly, so that the grease can be filled and replaced in a short time.

  Since the formation positions of the greasing port 144 and the draining port 146 are the farthest positions in the circumferential direction (the phase difference in the circumferential direction between the centers of the greasing port 144 and the draining port 146: 180 °), the grease The moving distance inside the reduction gear 100 is longer. For this reason, the grease supplied from the greasing port 144 moves evenly through the reduction gear 100 until reaching the draining port 146, and spreads through the reduction gear 100 to every corner.

  The first external gear 116 is formed with first and second through holes 152A and 154A and first to sixth inner pin holes 122A to 127A penetrating in the axial direction on the same circumference. Therefore, the first external gear 116 can be easily manufactured by simplifying the manufacturing process. The second and third external gears 118 and 120 can obtain the same effect (since they have the same configuration as the first external gear 116).

  Next, a second embodiment will be described.

  FIG. 5 shows a front view of an eccentric oscillating speed reducer 200 according to the second embodiment of the present invention.

  Also in the present embodiment, the supply / grease ports 244 and 246 are formed to penetrate the first flange body 234 in the axial direction, and the first and second through holes 252A and 254A are the first external teeth. A gear 216 is formed so as to penetrate in the axial direction. Similarly to the above embodiment, the second and third external gears 218 and 220 are also formed with third, fourth through holes 254B, fifth and sixth through holes 254C, respectively.

  In the present embodiment, the circumferential phase difference Z between the centers of the greasing port 244 and the draining port 246 is about 120 ° around the axis of the first flange body 234 (Z≈120 °). ). On the other hand, the circumferential phase difference between the centers of the first and second through holes 252A, 254A is 180 ° around the axis of the first external gear 216 (as in the above embodiment). (K = 180 °). The first through hole 252A is formed at a position that does not overlap with the greasing port 244 when viewed in the axial direction (circumferential phase difference (deviation amount): I °). On the other hand, the second through-hole 254A is formed at a position overlapping the fat removal port 246 when viewed in the axial direction (circumferential phase difference (deviation amount): 0 °). That is, the amount of deviation between the centers of the greasing port 244 and the first through hole 252A is larger than the amount of deviation between the centers of the grease discharging port 246 and the second through hole 254A.

  Generally, the amount of deviation (circumferential phase difference) between the through-hole of the external gear and the supply / grease port (formed on the flange disposed on the axial side portion of the external gear) The larger the grease, the harder it is to move in the axial direction. This is because the external gear has a greater resistance to the grease moving in the axial direction (prevents movement of the grease). On the other hand, the greater the amount of displacement between the through hole and the supply / grease port, the greater the amount of grease movement in the radial axis direction. This is because the grease collides with the axial wall surface of the external gear and moves in the radial direction of the reduction gear. That is, the speed reducer can control the grease movement direction and the amount of grease passing in each movement direction by the amount of deviation between the supply and drain ports and the through hole.

  In the present embodiment, since the first external gear 216 imparts moderate resistance to the grease moving in the axial direction (to further prevent the grease from moving in the axial direction), the grease movement path is Further, the reduction gear 200 is branched in the radial direction and the axial direction, and the grease can also move in the radial direction at an appropriate rate. As a result, the grease can be distributed evenly to every corner of the reduction gear 200.

  It should be noted that the circumferential phase difference (deviation amount) between the through hole and the fat drain opening may not be 0 ° as long as it is smaller than I °.

  Since the other configuration is basically the same as the structure of the eccentric oscillating speed reducer 100 shown in FIG. 1, the portion corresponding to the eccentric oscillating speed reducer 100 (functionally similar part) is Only two digits are given the same reference numerals, and redundant description is omitted.

  Similarly, in the eccentric oscillating speed reducer 100 according to the following embodiments, the lower two digits are assigned the same reference numerals in the portions corresponding to the structure of the eccentric oscillating speed reducer 100 shown in FIG. Description is omitted.

  Next, a third embodiment will be described.

  FIG. 6: shows the (A) front view and (B) longitudinal cross-sectional view of the eccentric rocking | swiveling type reduction gear 300 concerning the 3rd Embodiment of this invention.

  In the present embodiment, the first through hole 352A formed in the first external gear 316 is formed at a position that overlaps with the greasing port 344 formed in the first flange body 334 when viewed in the axial direction ( Phase difference in circumferential direction (deviation amount: 0 °). On the other hand, the second through-hole 354A formed in the first external gear 316 is formed at a position that does not overlap with the fat removal port 346 formed in the first flange body 334 when viewed in the axial direction (circumference). Directional phase difference (shift amount): P °). That is, the amount of deviation between the centers of the grease outlet 346 and the second through hole 354A is larger than the amount of deviation between the centers of the grease supply port 344 and the first through hole 352A. For this reason, in this embodiment, the drainage port 246 and the second drainage port 246 and the second (as in the case of the speed reducer (200) in the above embodiment) (based on the above-described relationship between the supply amount and the displacement amount of the drainage port and the through hole). Compared to a configuration in which the amount of deviation between the greasing port 244 and the first through hole 252A is larger than the amount of deviation from the through hole 254A, the enclosed grease moves more in the axial direction of the speed reducer 300. It becomes easy to enclose in the internal space of the speed reducer 300, and more easily moves in the radial direction before being discharged from the oil drain port 346.

  From the above, the speed reducer 300 can enclose the grease in the speed reducer 300 more efficiently than the speed reducer (200).

  Note that the circumferential phase difference (shift amount) between the through hole and the greasing port may not be 0 ° as long as it is smaller than P °.

  Next, fourth and fifth embodiments will be described.

  FIG. 7A shows a longitudinal sectional view of an eccentric oscillating speed reducer 400 according to the fourth embodiment of the present invention.

  As shown in FIG. 7A, the first external gear 416 has three first to third through holes 452A, 454A, and 456A formed at equal intervals on the same circumference. The number of through holes is larger than in the above embodiment. For this reason, the grease movement path is distributed to the first to third through holes 452A, 454A, 456A formed at equal intervals, and the grease moves in the radial direction and the axial direction of the speed reducer 400 in a well-balanced manner. That is, the speed reducer 400 increases the degree of freedom of the grease movement path, so that the grease can move more flexibly, and the grease can be evenly distributed inside the speed reducer 400.

  Next, a fifth embodiment will be described.

  FIG. 7B shows a longitudinal sectional view of an eccentric oscillating speed reducer 500 according to the fifth embodiment of the present invention.

  As shown in FIG. 7 (B), six first to sixth through holes 552A, 554A, 556A, 558A, on the axial side surface of the first external gear 516 of the eccentric oscillating speed reducer 500, 560A and 562A are formed at equal intervals on the same circumference. In this case, since the number of through holes is larger than that in the above embodiment, the movement of the grease inside the speed reducer 500 can be further improved. As a result, the same effect as the above embodiment can be obtained.

  In the fourth and fifth embodiments, the through hole formed in the external gear may be formed at a position that overlaps the supply and drainage ports formed in the flange as viewed in the axial direction. You may form in the position which does not become.

  Next, a sixth embodiment will be described.

  FIG. 8: shows the (A) front view, (B) rear view, and (C) longitudinal cross-sectional view of the eccentric rocking | swiveling type reduction gear 600 concerning the 6th Embodiment of this invention.

  In the present embodiment, the greasing port 644 is formed through the first flange body 634 in the axial direction. The oil drain port 646 is formed through the second flange body 636 in the axial direction. Further, a first through hole (not shown) and a second through hole 654A are formed through the first external gear 616 in the axial direction. The grease supplied from the greasing port 644 is supplied from the first flange body 634 side to the first, third, and fifth through holes (not shown) of the first to third external gears 616, 618, and 620 and the second, While arbitrarily passing through the fourth and sixth through holes 654A, 654B, and 654C, it reaches every corner of the speed reducer 600, and the old grease moves toward the grease outlet 646 of the second flange body 636, and is discharged. It is discharged from the oil port 646. As a result, the same effect as the above embodiment can be obtained.

  In addition, you may reverse the relationship of the supply position with respect to a 1st, 2nd flange body, and the formation position of a fat removal port.

  Next, a seventh embodiment will be described.

  FIG. 9: shows the (A) front view and (B) longitudinal cross-sectional view of the eccentric rocking | swiveling type reduction gear 700 concerning the 7th Embodiment of this invention.

  In the speed reducer 700, the inner pin 770 formed integrally with the first flange body 734 is not connected to the second flange body 736, and only the first flange body 734 has the first to third outer teeth. It synchronizes with the rotation component of the gears 716, 718, 720. Also in this embodiment, the supply / grease ports 744 and 746 are formed through the first flange body 734 in the axial direction. Further, a first through hole (not shown) and a second through hole 754A are formed through the first external gear 716 in the axial direction. Similarly to the above embodiment, the second and third external gears 718 and 720 are also formed with third, fourth through holes 754B, fifth and sixth through holes 754C, respectively. Accordingly, the grease passes through the first to sixth through holes 752A, 754A, 754B, and 754C of the first to third external gears 716, 718, and 720, and as a result, the same effect as that of the above embodiment is obtained. be able to.

  In the above-described embodiment, several through holes are formed through the external gear in the axial direction. However, the present invention is not limited to this. For example, as the through holes, several tens (or several hundreds) are formed. ) You may make it form a very small through-hole (through-hole much smaller than the diameter of the through-hole shown in the said embodiment) in an external gear. When a plurality of through holes are formed, the through holes may be formed on different circumferences. Further, the opening area of only some of the specific through holes may be increased, and the opening areas of the through holes may be different.

  In addition, in the said embodiment, although a supply and a fat removal port are formed in the 1st, 2nd flange body, it is not restricted to this, For example, it is made to form either a supply or a fat discharge port in a casing, for example It may be. For example, when the greasing port is installed in the casing in the radial direction and the greasing port is installed in the axial side surface of the flange, the grease supplied from the greasing port is centered in the radial direction along the axial side surface of the external gear. Then, it passes through the through-hole of the external gear, moves in the speed reducer also in the axial direction, and is discharged from the fat outlet. As a result, the grease is supplied to the entire internal space of the speed reducer.

  In the above embodiment, the eccentric oscillating type speed reducer is an eccentric oscillating type speed reducer in which one eccentric body shaft is arranged at the shaft center of the speed reducer. The present invention can also be applied to a so-called sort-type eccentric oscillating type speed reducer in which the eccentric body shaft is arranged offset from the axis of the speed reducer. Moreover, in the said embodiment, although a reduction gear is a reduction gear provided with the reduction mechanism of 1 step | paragraph, the reduction gear which can apply this invention is not restricted to this, The reduction speed reduction provided with the reduction mechanism of 2 steps | paragraphs or more A machine may be used. In this case, any of the speed reduction mechanisms is not limited to the eccentric oscillation type speed reduction mechanism, and may be a speed reduction mechanism of an orthogonal gear or a parallel shaft gear.

  Moreover, in the said embodiment, as a reduction gear, it is a reduction gear with which the rotation component of an external gear and the flange arrange | positioned at the axial direction side part of this external gear are synchronizing, Comprising: Although a reduction gear that rotates on the gear side is employed, a reduction gear that rotates on the casing side (internal gear side) may be used. Furthermore, not limited to this, for example, as described in Patent Document 1 (see FIG. 10), the speed at which the flange rotates without being synchronized with the rotation component of the external gear or is fixed to an external member. The present invention can also be applied to a machine.

  The present invention is effective when encapsulating hard grease inside the speed reducer. However, the present invention is not limited to this, and can also be applied when encapsulating soft grease inside the speed reducer.

DESCRIPTION OF SYMBOLS 100 ... Reducer 116, 118, 120 ... External gear 130 ... Internal gear 134 ... Flange 144 ... Grease port 146 ... Grease port 152A, 154A, 154B, 154C ... Through-hole

Claims (8)

An external gear that eccentrically swings, an internal gear that has a slight difference in the number of teeth from the external gear of the external gear, and an internal gear that is internally meshed with the external gear; and In an eccentric oscillating type speed reducer provided with a flange disposed on an axial side,
The flange is formed with at least one of a greasing port for supplying grease sealed inside the speed reducer and a greasing port for discharging the grease, and
An eccentric oscillating speed reducer, wherein a through hole through which the component of the speed reducer is not inserted is formed in the external gear through the external gear in the axial direction. In claim 1,
A plurality of the through holes are formed in the external gear. An eccentric oscillating type speed reducer. In claim 2,
The plurality of through-holes are formed at equal intervals on the same circumference. An eccentric oscillating speed reducer. In any one of Claims 1-3,
The greasing port is formed in the flange;
An eccentric oscillating speed reducer, wherein an opening area of the through hole formed in the external gear is larger than an opening area of a greasing port formed in the flange. In any one of Claims 1-4,
The flange is synchronized with the rotation component of the external gear, and the grease port is formed in the flange.
The eccentric oscillating speed reducer, wherein the through-hole formed in the external gear is formed at a position overlapping with a greasing port formed in the flange as viewed in the axial direction. In any one of Claims 1-5,
The flange is synchronized with the rotation component of the external gear, and the drainage port is formed in the flange.
The eccentric oscillating speed reducer, wherein the through-hole formed in the external gear is formed at a position that does not overlap with a drain port formed in the flange when viewed in the axial direction. In any one of Claims 1-6,
The flange is synchronized with the rotation component of the external gear, and both the greasing port and the greasing port are formed on the flange.
An eccentric oscillation type speed reducer characterized in that a circumferential phase difference between the centers of the greasing port and the draining port centering on the axis of the flange is 180 °. In any one of Claims 1-7,
The flange is synchronized with the rotation component of the external gear, and both the greasing port and the greasing port are formed in the flange,
And at least the center of the drainage port and the through hole are deviated, and
An eccentric oscillating type speed reducer characterized in that the amount of deviation between the center of the grease outlet and the through hole is larger than the amount of deviation between the centers of the grease supply port and the through hole.

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