JP2009228783A - Rolling element retainer - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To supply a rolling element retainer capable of facilitating the manufacturing of a gear wheel using a rolling element as convex teeth. <P>SOLUTION: Before equipped to a first gear wheel g1 body, an inner diameter side retaining frame g13 and an outer diameter side retaining frame g14 are coupled by a coupling member 71 to form the rolling element retainer 7. Grooves 72, 73 which are arranging structures for arranging the rolling elements are respectively formed on the inner diameter side retaining frame g13 and the outer diameter side retaining frame g14 at equal intervals in a rotating direction of the first gear wheel g1. Furthermore, when the rolling element retainer 7 is equipped to the first gear train, parts becoming output sides of the grooves 72, 73 are provided with a tilting structure formed so as to gradually increase a clearance between the inner diameter side retaining frame g13 and the outer diameter side retaining frame g14 toward the output sides. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a rolling element cage, and more particularly, to a rolling element cage for a gear that is used by being mounted on a gear that uses the rolling element as convex teeth.

  A speed reducer using a rocking gear device has been conventionally used as a transmission that is small in size and has a high reduction ratio and high transmission efficiency (for example, Patent Document 1). An example will be described with reference to FIGS.

  The substantially cylindrical first input shaft 101 is rotatably supported by a substantially cylindrical housing 104 via a bearing 111 and a bearing 121. Further, a first gear g101 (shaft gear), which is a bevel gear, is fixed to the first input shaft 101 with the tooth surface in the axial direction facing the output side (hereinafter simply referred to as “output side”) in the output shaft direction. ing. A bearing gear 105 as a rotating member is disposed on the output side of the first gear g101, and the input side in the axial direction of the inner ring 151 of the bearing gear 105 (hereinafter simply referred to as “input side”). Is formed with a second gear g102 (rotating member gear) which is a face gear. Since the second gear g102 meshes with the first gear g101, the rotational force of the first input shaft 101 is transmitted to the bearing gear 105 when the first input shaft 101 is rotating. An outer ring 152 is provided so as to surround the circumferential portion of the inner ring 151 from the outer side (hereinafter simply referred to as “outer side”) in the radial direction, and between the inner ring 151 and the outer ring 152. A bearing gear 105, which is a bearing-integrated gear, is formed by interposing the rolling elements 153.

  A third gear g103 (rotating member gear) that is a face gear is formed on the output side (hereinafter simply referred to as “output side”) in the axial direction of the inner ring 151 of the bearing gear 105. Further on the output side of the third gear g103, the output shaft 3 is rotatably supported on the housing 104 via the bearing 22 and the bearing 23. A fourth gear g104, which is a bevel gear, is fixed to the output shaft 3 with the tooth surface facing the input side in the axial direction. Since the above-described third gear g103 is engaged with the fourth gear g104, the rotational force transmitted to the bearing gear 105 is transmitted to the output shaft 3. The first input shaft 101 and the output shaft 3 have the same rotating shaft 6.

  The first gear g101 is formed with a semi-cylindrical concave groove g111, and a cylindrical rolling element g112 is supported in the concave groove g111 so as to allow rolling. Since the cylindrical rolling element g112 is supported by the semi-cylindrical concave groove g111, approximately half of the outer peripheral surface of the rolling element g112 protrudes toward the second gear g102, and this protruding portion is the first gear. It functions as a convex tooth of g101. On the other hand, a concave groove similar to the concave groove g111 formed in the first gear g101 is formed in the second gear g102. This concave groove functions as a concave tooth of the second gear g102.

More specifically, as shown in FIGS. 10A and 10B, the rolling element g112 inserted into the concave groove g111 can be rolled by the inner diameter side retainer g113 and the outer diameter side retainer g114. The first gear g101 has a structure to hold. The first gear g101 is manufactured as follows. That is, as shown in FIGS. 8A and 8B, first, the main body of the first gear g101 before mounting the rolling element g112 is arranged so that the groove g111 is as horizontal as possible. Next, as shown in FIGS. 9A and 9B, the rolling elements g112 are arranged one by one in the groove g111. Finally, as shown in FIG. 10A and FIG. 10B, the inner side is held at the end g116 of the first gear g101 body inward in the radial direction (hereinafter simply referred to as “inward”). An outer diameter side retainer g114 is attached to the outer end g117 of the main body of the first gear g101, and the rolling element g112 is held in the concave groove g111 so that it can roll.
JP 2006-46405 A

  In the manufacturing process of the first gear g101, first, the main body of the first gear g101 is arranged so that the concave groove g111 is as horizontal as possible. However, since the first gear g101 is a bevel gear, it should be completely horizontal. The concave groove g111 is inclined outward by the inclination angle of the umbrella of the bevel gear. The operation of arranging the rolling elements g112, which are fine structures, in the inclined concave groove g111 is a complicated operation. Moreover, since the rolling elements g112 are supported only by friction in the inclined grooves g111 during the arrangement work, they easily slide down due to slight vibrations or the like. This sliding operation makes the arrangement work more complicated. Further, the rolling element g112 may slide down when the inner diameter side retainer g113 and the outer diameter side retainer g114 are mounted on the respective end portions g116 and g117 of the first gear g101 main body. For example, if the inner diameter side retainer g113 is to be mounted first, the rolling element g112 may slide outwardly not held by the inner diameter side retainer g113. If the inner diameter side retainer g113 and the outer diameter side retainer g114 are integrated by connecting them with a member, the inner diameter side retainer g113 and the outer diameter side retainer g114 can be simultaneously mounted on the main body of the first gear g101. Is possible. Therefore, by attaching either one of the inner diameter side cage g113 and the outer diameter side cage g114 first, it is possible to prevent the rolling element g112 from sliding outward or inward without being held. However, the connecting portion must be provided on the tooth surface of the first gear g101, and the connecting portion is sandwiched between the meshing surfaces of the first gear g101 and the second gear g102, which impairs the function of the gear device. Furthermore, since the rolling element g112 easily slides down due to vibration, it is difficult to mechanize the manufacturing process of the first gear g101.

  Although illustration and detailed description are omitted, in the manufacturing process of the fourth gear g104, for the same reason, the rolling elements g112 easily slide down, so that the arrangement work of the rolling elements g112 is complicated. Moreover, the rolling-down of the rolling element g112 can also occur when the inner diameter side cage g113 and the outer diameter side cage g114 are attached to the respective ends of the fourth gear g104 main body. For example, when trying to attach the inner diameter side cage first, the rolling element g112 may slide outward. If the inner diameter side cage and the outer diameter side cage are integrated by communicating with each other by a member, the inner diameter side cage and the outer diameter side cage can be simultaneously mounted on the fourth gear g104 main body. . Therefore, it is possible to prevent the rolling elements from slipping outward or inward by attaching one of the inner diameter side retainer and the outer diameter side retainer first. However, the connecting portion must be provided on the tooth surface of the fourth gear g104, and the connecting portion is sandwiched between the meshing surfaces of the fourth gear g104 and the third gear g103, which impairs the function of the gear device. Furthermore, since the rolling element g112 easily slides down due to vibration, it is difficult to mechanize the manufacturing process of the fourth gear g104.

  Therefore, the present invention has been made in view of such circumstances, and an object of the present invention is to provide a rolling element cage capable of facilitating the manufacture of a gear using the rolling elements as convex teeth as compared with the conventional one. .

  A rolling element cage according to the present invention is used in an oscillating gear device, and has a semi-cylindrical concave groove formed at equal intervals in the rotation direction, and a substantially cylindrical shape supported so as to be able to roll in the concave groove. A rolling element holder for holding the rolling element, the rolling element being mounted on a gear using the rolling element as a convex tooth. An inner diameter side holding frame that holds the rolling element from the inside in the radial direction of the gear; an outer diameter side holding frame that holds the rolling element from the outer side in the radial direction of the gear; and the inner diameter side holding frame And a connecting member that connects the outer diameter side holding frame. Further, the inner diameter side holding frame and the outer diameter side holding frame have an arrangement structure for arranging the rolling elements at a position corresponding to the concave groove, and in the state where the rolling element is mounted, The member has a detachable structure that can be detached from the inner diameter side holding frame and the outer diameter side holding frame.

  According to the above configuration, since the inner diameter side holding frame and the outer diameter side holding frame have an arrangement structure for arranging the rolling elements at positions corresponding to the concave grooves, before attaching the rolling element holder to the gear, The rolling element can be disposed in the rolling element holder. In addition, since the rolling element is disposed at a position corresponding to the concave groove, the rolling element can be supported in the concave groove so as to be able to roll by attaching the rolling element retainer provided with the rolling element to the gear. It becomes possible. Therefore, it is not necessary to arrange rolling elements in a semi-cylindrical concave groove formed in the gear, and a gear using the rolling elements as convex teeth can be easily manufactured as compared with the conventional one.

  In addition, according to the above configuration, since the connecting member has a detachable structure in which the connecting member can be removed in the state where the connecting member is mounted on the gear, the connecting member is positioned on the meshing surface of the gear so that the connecting member is connected when meshing with another gear. The member is prevented from being caught.

  In the rolling element cage according to the present invention, the detaching structure is formed by reducing the shear strength of at least a part of the connecting member as compared with the inner diameter side holding frame and the outer diameter side holding frame. It is preferable.

  According to the above configuration, the detaching structure is formed by reducing the shear strength of at least a part of the connecting member as compared with the inner diameter side holding frame and the outer diameter side holding frame. It is possible to easily reduce the shear strength by reducing the cross-sectional area of the portion as compared with, for example, the inner diameter side holding frame and the outer diameter side holding frame. Therefore, the detachable structure can be configured at a general purpose and inexpensively.

  In the rolling element cage according to the present invention, it is preferable that the arrangement structure is a groove for inserting the rolling element.

  Since the arrangement structure is a groove for inserting the rolling elements, the arrangement structure can be realized with a simple configuration.

  In the rolling element retainer according to the present invention, it is preferable that an inclined structure for guiding the rolling element into the groove is formed in the inner diameter side holding frame and the outer diameter side holding frame.

  Since the inclined structure for guiding the rolling element to the groove is formed in the inner diameter side holding frame and the outer diameter side holding frame, the rolling element can be easily disposed in the rolling element holder.

  ADVANTAGE OF THE INVENTION According to this invention, it becomes possible to supply the rolling element holder improved so that the gear which uses a rolling element as a convex tooth can be manufactured easily compared with the said conventional.

  The structure of the oscillating gear device according to this embodiment will be described below with reference to the drawings.

  As shown in FIG. 1, the oscillating gear device according to the present embodiment includes a substantially cylindrical housing 4, a substantially columnar first input shaft 1 inserted into the housing, and a substantially cylindrical second input. The shaft 2 includes a substantially cylindrical output shaft 3 and first to fourth gears, which are supported via bearings. That is, it is a rocking gear device having two input shafts and one output shaft.

  The substantially cylindrical first input shaft 1 is rotatably supported by a substantially cylindrical housing 4 via a bearing 11 and a bearing 12. The first input shaft 1 has a first gear g1 (shaft gear), which is a bevel gear, with the tooth surface facing the output side in the axial direction (hereinafter simply referred to as “output side”) in the output shaft direction. It is fixed. A bearing gear 5 that is a rotating member is disposed on the output side of the first gear g1, and the input side in the axial direction of the inner ring 51 of the bearing gear 5 (hereinafter simply referred to as “input side”). Is formed with a second gear g2 (rotating member gear) which is a face gear. Since the second gear g2 meshes with the first gear g1, the rotational force of the first input shaft 1 is transmitted to the bearing gear 5 when the first input shaft 1 is rotating. An outer ring 52 is provided so as to surround the circumferential portion of the inner ring 51 from the outside (hereinafter simply referred to as “outside”) in the radial direction, and between the inner ring 51 and the outer ring 52. A bearing gear 5 that is a bearing-integrated gear is formed by interposing the rolling elements 53.

  A third gear g3 (rotating member gear) that is a face gear is formed on the output side of the inner ring 51 of the bearing gear 5. Further on the output side of the third gear g3, the output shaft 3 is rotatably supported by the housing 4 via a bearing 22 and a bearing 23. Further, a fourth gear g4 (shaft gear), which is a bevel gear, is fixed to the output shaft 3 with the tooth surface facing the input side in the axial direction. Since the fourth gear g4 is engaged with the third gear g3, the rotational force transmitted to the bearing gear 5 is transmitted to the output shaft 3. The first input shaft 1 and the output shaft 3 have the same rotation shaft 6.

  A substantially cylindrical second input shaft 2 is supported on the housing 4 via a bearing 22 and a bearing 23 so as to surround the first gear g1 to the fourth gear g4 from the outside. The inner peripheral surface 21 of the second input shaft 2 has a cylindrical shape that is eccentric with respect to the rotation shaft 6. Further, the outer ring 52 of the above-described bearing gear 5 is fitted into the inner peripheral surface 21. As a result, the outer ring 52 and the bearing gear 5 are provided in an eccentric state with respect to the rotating shaft 6.

  First, the relationship between the input from the first input shaft 1 and the second input shaft 2 and the output shaft 3 will be described.

  First, the case where the second input shaft 2 is fixed and the first input shaft 1 is in the rotating state in the state of FIG. 1 will be described. Since the second input shaft 2 is fixed, the outer ring 52 of the bearing gear 5 fitted therein is also fixed. Therefore, the bearing gear 5 is kept in a state where its rotation shaft is fixed. In this state, the rotational force of the first input shaft 1 is transmitted to the bearing gear 5 via the first gear g1 and the second gear g2, and the rotational force transmitted to the bearing gear 5 is transmitted to the third gear. Since the torque is transmitted to the output shaft 3 via g3 and the fourth gear g4, the rotational force of the first input shaft 1 is decelerated according to the gear ratio of the first gear g1 to the fourth gear g4, and the output shaft 3 Is transmitted to.

  Next, the case where the first input shaft 1 is fixed and the second input shaft 2 is in the rotating state in the state of FIG. 1 will be described. Since the second input shaft 2 rotates, the outer ring 52 of the bearing gear 5 fitted therein also rotates. Here, since the inner peripheral surface 21 of the second input shaft 2 has a cylindrical shape that is eccentric with respect to the rotating shaft 6, the entire bearing gear 5 changes the eccentric shaft via the outer ring 52. A rotating rocking motion is performed. Here, since the first input shaft 1 is fixed, the rotational force of the second input shaft 2 is transmitted to the bearing gear 5 through the outer ring 52, and the rotational force transmitted to the bearing gear 5 is Since the torque is transmitted to the output shaft 3 via the third gear g3 and the fourth gear g4, the rotational force of the input shaft 2 is decelerated according to the gear ratio of the first gear g1 to the fourth gear g4 and output shaft. 3 is transmitted. Thus, when either the first input shaft 1 or the second input shaft 2 is fixed, the rotational force from the unfixed input shaft is the gear ratio of the first gear g1 to the fourth gear g4. Is decelerated accordingly and transmitted to the output shaft 3.

  Furthermore, the case where the 1st input shaft 1 and the 2nd input shaft 2 are in the rotation state in the state of FIG. 1 is demonstrated. In this case, the rotational force of the second input shaft 2 is transmitted to the output shaft 3 by swinging the entire bearing gear 5, and the rotational force of the first input shaft 1 is also transmitted to the output shaft 3. . Therefore, the resultant force of the rotational force of the first input shaft 1 and the rotational force of the second input shaft 2 can be transmitted to the output shaft 3. As described above, when neither the first input shaft 1 nor the second input shaft 2 is fixed, the rotational force from the first input shaft 1 and the second input shaft 2 becomes the first gear g1. ~ Decelerated according to the gear ratio of the fourth gear g4 and transmitted to the output shaft 3. That is, the rotational force of the output shaft 3 can be freely changed by controlling the rotational force of the first input shaft 1 and the rotational force of the second input shaft 2, respectively.

  Next, the reduction ratio will be described separately for each case. First, the case where the second input shaft 2 is fixed and the first input shaft 1 is in a rotating state will be described. The rotation of the first input shaft 1 is transmitted to the bearing gear 5 in accordance with the ratio of the number of teeth n1 of the first gear g1 and the number of teeth n2 of the second gear g2, that is, n1 / n2. For example, if the number of teeth n1 of the first gear g1 is 100 and the number of teeth n2 of the second gear g2 is 102, the first input shaft 1 makes one revolution and the first gear g1 makes one revolution. The two gears g2 rotate 100/102, and the rotation of the first input shaft 1 is transmitted to the bearing gear 5. That is, in this case, the first stage deceleration of 100/102 is performed.

  Similarly, the rotation of the second input shaft 2 is transmitted to the bearing gear 5 corresponding to the ratio of the number of teeth n3 of the third gear g3 and the number of teeth n4 of the fourth gear g4, that is, n3 / n4. For example, if the number of teeth n3 of the third gear g3 is 110 and the number of teeth n4 of the fourth gear g4 is 112, the inner ring 51 of the bearing gear 5 rotates once and the third gear g3 rotates once. The four gears g4 rotate 110/112, and the rotation of the first input shaft 1 is transmitted to the bearing gear 5. That is, in this case, 110/112 second-stage deceleration is performed. Therefore, the rotation of the first input shaft 1 is decelerated at a reduction ratio of n3 / n4 × n1 / n2 = (n1 · n3) / (n2 · n4) due to the deceleration of the first stage and the second stage. It becomes. In the above example, a reduction ratio of 110/112 × 100/102 = (100 · 110) / (102 · 112) ≈0.963, that is, about 96.3% is obtained.

  Next, a case where the first input shaft 1 is fixed and the second input shaft 2 is in a rotating state will be described. The rotation of the second input shaft 2 is transmitted to the bearing gear 5 corresponding to the difference between the number of teeth n1 of the first gear g1 and the number of teeth n2 of the second gear g2, that is, n2−n1. For example, if the number of teeth n1 of the first gear g1 is 100 and the number of teeth n2 of the second gear g2 is 102, the second input shaft 2 makes one rotation and the bearing gear 5 makes one rotation. The rotation of the second input shaft 2 is transmitted to the bearing gear 5 as the gear g2 rotates 102-100, that is, two teeth. Therefore, the reduction ratio is (n2-n1) / n2. That is, in this case, the first-stage deceleration of (102-100) / 102 is performed.

When the second input shaft 2 is in the rotating state, on the one hand, the second input shaft corresponds to the difference between the number of teeth n4 of the fourth gear g4 and the number of teeth n3 of the third gear g3, that is, n4-n3. The rotation of 2 is transmitted to the output shaft 3 via the bearing gear 5. For example, if the number of teeth n3 of the third gear g3 is 110 and the number of teeth n4 of the fourth gear g4 is 112, the inner ring 51 of the bearing gear 5 makes one rotation and the third gear g3 makes one rotation. The rotation of the second input shaft 2 is transmitted to the output shaft 3 as the four gears g4 rotate 112-110, that is, two teeth. Therefore, the reduction ratio is (n4-n3) / n4. Here, since the number of rotations of the third gear g3 is reduced by the ratio between the number of teeth n1 of the first gear g1 and the second gear g2 by the first-stage deceleration, (n4−n3) / n4 × n1 / n2 That is, in this case, the second-stage deceleration of (112−110) / 112 × 100/102 is performed. Therefore, combining the first stage deceleration and the second stage deceleration,
(N2-n1) / n2 + (n4-n3) / n4 × n1 / n2
That is, (102-100) / 102 + (112-110) / 112 × 100/102
≒ 0.0196 + 0.0175
= 0.0371
That is, a reduction ratio of about 3.71% is obtained.

  As described above, the reduction gear ratio can be freely changed by changing the number of teeth n1 to n4 of the first gear g1 to the fourth gear g4, and is particularly large for the input from the second input shaft 2. The reduction ratio can be easily obtained.

  Here, the oscillating gear device according to the present embodiment is characterized in that the shape of the rolling element holder for holding the rolling elements used in the shaft gear is improved. This will be described below. FIG. 2A schematically shows the meshing portion between the first gear g1 and the second gear g2, and FIG. 2B shows the meshing portion between the first gear g1 and the second gear g2 in an enlarged manner. As described above, the first gear g1 is formed with a semi-cylindrical concave groove g11, and a cylindrical rolling element g12 is supported by the concave groove g11 so as to be able to roll. Since the cylindrical rolling element g12 is supported by the semi-cylindrical concave groove g11, approximately half of the outer peripheral surface of the rolling element g12 protrudes toward the second gear g2, and this protruding portion is the first gear. It functions as a convex tooth of g1. On the other hand, a concave groove g21 similar to the concave groove g11 formed in the first gear g1 is formed in the second gear g2. The concave groove g21 functions as a concave tooth of the second gear g2. That is, the portion of the rolling element g12 that protrudes toward the second gear g2 meshes with the concave groove g21 of the second gear g2. Therefore, the sliding that occurs when the rolling element g12 and the concave groove g21 are engaged is absorbed by the rolling of the rolling element g12 indicated by an arrow in FIG. Therefore, since it is not necessary to provide a backlash, it is possible to precisely adjust the meshing and reduce vibration and noise. In addition, since a preload can be applied between the gears, the meshing adjustment can be performed more precisely, and vibration and noise can be reduced. Further, the loss of rotational force is reduced.

  More specifically, as shown in FIG. 6, the first gear g1 has a structure in which the rolling elements g12 inserted in the concave grooves g11 are rotatably held by the inner diameter side holding frame g13 and the outer diameter side holding frame g14. Has. Here, as shown in FIG. 3, before the first gear g1 is mounted, the inner diameter side holding frame g13 and the outer diameter side holding frame g14 are connected by the connecting member 71 to form the rolling element holder 7. Yes. The inner diameter side holding frame g13 and the outer diameter side holding frame g14 are provided with grooves 72 and 73, which are arrangement structures for arranging the rolling elements g12, at equal intervals in the rotation direction Y of the first gear g1. Yes. Further, pawls 74 and 75 for mounting the rolling element holder 7 on the first gear g1 main body are extended between the grooves 72 and 73 and the grooves 72 and 73 in the axial direction. Furthermore, when the rolling element holder 7 is mounted on the first gear g1, the gap between the inner diameter side holding frame g13 and the outer diameter side holding frame g14 is directed to the output side in the portion which becomes the output side of the grooves 72 and 73. Inclined structures 76 and 77 are formed so as to increase gradually as the time elapses.

  The manufacturing process of the 1st gear g1 using this rolling element holder | retainer 7 is as follows. First, as shown in FIG. 5A which is an AA cross-sectional view in FIGS. 4 and 4, the rolling element g <b> 12 is fitted into the grooves 72 and 73 of the rolling element holder 7 from the output side. At this time, since the rolling element g12 is supported by the grooves 72 and 73, sliding or dropping does not easily occur. Further, the rolling elements g12 can be easily introduced into the grooves 72 and 73 by the inclined structures 76 and 77 provided at the output side portions of the grooves 72 and 73. When the required number of rolling elements g12 are fitted in the grooves 72 and 73 of the rolling element holder 7, the rolling element holder 7 and the rolling element g12 are integrated.

  Next, the integrated rolling element holder 7 and rolling element g12 are mounted on the first gear g1 body. Further, as shown in FIG. 5B, which is a BB cross-sectional view in FIG. 4, the claws 74 and 75 of the rolling element retainer 7 are formed so as to be close to each other, so that they are attached to the first gear g1 body. In the state, as shown in FIG. 5C, which is a cross-sectional view taken along the line B-B in a state where the rolling element cage 7 is mounted on the first gear, the claws 74 and 75 are engaged with the concave portion 81 of the first gear g1 body. be able to. After mounting the rolling element holder 7, the connecting member 71 is removed. Here, the connecting portion 71a between the connecting member 71 and the inner diameter side holding frame g13 and the connecting portion 71b between the connecting member 71 and the outer diameter side holding frame g14 are compared to the inner diameter side holding frame g13 and the outer diameter side holding frame g14. And since it has a small cross section, it has a structure with low shear strength. Therefore, by applying a shearing force to the connection portion 71a and the connection portion 71b, the connection member 71 that is no longer needed can be removed without damaging the inner diameter side holding frame g13 and the outer diameter side holding frame g14. Thus, by removing the connecting member 71, it is possible to prevent the connecting member 71 from being sandwiched between the meshing surfaces of the first gear g1 and the second gear g2 and impairing the function as the gear device.

  Since the structure and manufacturing method of the fourth gear g4 are the same as those of the first gear g1, illustration and detailed description thereof will be omitted.

  According to the oscillating gear device of the above embodiment, the following effects can be obtained.

  (1) According to the oscillating gear device of the above embodiment, the inner diameter side holding frame g13 and the outer diameter side holding frame g14 are arranged to arrange the rolling elements g12 at positions corresponding to the concave grooves g11. Therefore, the rolling element g12 can be disposed in the rolling element holder 7 before the rolling element holder 7 is attached to the first gear g1. Moreover, since the rolling element g12 is arrange | positioned in the position corresponding to the ditch | groove g11, by attaching the rolling element holder 7 in which the rolling element g12 was arrange | positioned to the 1st gear g1, the rolling element g12 is made into the ditch | groove g11. Can be supported so as to be able to roll. Therefore, it is not necessary to arrange the rolling elements g12 in the semi-cylindrical concave grooves g11 formed in the first gear g1, and the first gear g1 using the rolling elements g12 as convex teeth is easily manufactured as compared with the conventional one. be able to.

  (2) According to the oscillating gear device of the above embodiment, the connecting member 71 has a detachable structure in which the connecting member 71 can be removed when the connecting member 71 is attached to the first gear g1, so that the connecting member 71 is provided on the meshing surface of the first gear g1. The positioning of the connecting member 71 prevents the connecting member 71 from being caught when meshing with the second gear g2.

  (3) According to the oscillating gear device of the above-described embodiment, the connection portions 71a and 71b of the connecting member 71 have a smaller shear strength than the inner diameter side holding frame g13 and the outer diameter side holding frame g14. It has a formed removal structure. Since the detaching structure provided in the connection portions 71a and 71b is realized by reducing the cross-sectional area of the portion compared to the inner diameter side holding frame and the outer diameter side holding frame, it can be easily formed. Therefore, the detachable structure can be configured at a general purpose and inexpensively.

  (4) According to the oscillating gear device of the above embodiment, since the arrangement structure for arranging the rolling element g12 is the grooves 72 and 73 for fitting the rolling element g12, it has a simple configuration. An arrangement structure can be realized.

  (5) According to the oscillating gear device of the above embodiment, the inclined structures 76 and 77 for guiding the rolling element g12 to the grooves 72 and 73 are formed on the inner diameter side holding frame g13 and the outer diameter side holding frame g14. Therefore, it is easy to dispose the rolling element g12 in the rolling element holder 7.

  In addition, you may change the said embodiment as follows.

  In the above embodiment, the inclined structures 76 and 77 are provided on the output side portions of the grooves 72 and 73, but other configurations may be used. For example, another structure for introducing the rolling element g12 may be provided, or a special structure may not be provided if it is not difficult to introduce the rolling element g12.

  In the above embodiment, the grooves 72 and 73 are provided as the arrangement structure for arranging the rolling elements g12, but the rolling elements g12 are arranged at positions on the rolling element holder corresponding to the concave grooves g11. Any other structure may be used as long as it is an arrangement structure.

  In the above embodiment, the present invention is applied to an oscillating gear device having two input shafts and one output shaft. However, the present invention is applied to an oscillating gear device having one input shaft and one output shaft. The present invention may be applied. For example, the first gear g1 may be fixed to the housing and input from only the second input shaft.

  Since the present invention relates to a rolling element holder that is easy to manufacture, the present invention can be widely used for small devices that require a high reduction ratio.

It is drawing explaining one Embodiment of the rocking | swiveling gear apparatus which employ | adopted the rolling element holder concerning this invention, Comprising: It is an axial sectional view. BRIEF DESCRIPTION OF THE DRAWINGS It is drawing explaining one Embodiment of the rocking | fluctuation type gear apparatus which employ | adopted the rolling element holder | retainer concerning this invention, Comprising: (a) is the elements on larger scale about the meshing part of a 1st gear-a 4th gear. (B) is an enlarged view about the meshing part of a 1st gearwheel and a 2nd gearwheel. It is drawing explaining one Embodiment of the rolling element holder concerning this invention, Comprising: It is the figure which looked at the rolling element holder from the output side. It is drawing explaining one Embodiment of the rolling element holder concerning this invention, Comprising: It is a figure which shows the state which has arrange | positioned the rolling element to the rolling element holder. It is drawing explaining one Embodiment of the rolling element holder | retainer concerning this invention, Comprising: (a) is AA sectional drawing in FIG. 4, (b) is BB sectional drawing in FIG. (C) is BB sectional drawing in the state which mounted | wore the 1st gearwheel with the rolling element holder | retainer. BRIEF DESCRIPTION OF THE DRAWINGS It is drawing explaining one Embodiment of the rolling element holder concerning this invention, Comprising: It is the elements on larger scale which show the state which mounted | wore the 1st gearwheel with the rolling element holder. It is drawing explaining one Embodiment of the rocking | fluctuation type gear apparatus which employ | adopted the conventional rolling element holder, Comprising: It is an axial sectional view. BRIEF DESCRIPTION OF THE DRAWINGS It is drawing explaining one Embodiment of the rocking | fluctuation type gear apparatus which employ | adopted the conventional rolling element holder | retainer, Comprising: (a) is a partial expansion perspective view of a 1st gearwheel, (b) is A in (a). It is -A sectional drawing. It is drawing explaining one Embodiment of the rocking | fluctuation type gear apparatus which employ | adopted the conventional rolling element holder, Comprising: (a) is the elements on larger scale of the 1st gear in the state which arranged the rolling elements, (b) ) Is an AA cross-sectional view in (a). It is drawing explaining one Embodiment of the rocking | fluctuation type gear apparatus which employ | adopted the conventional rolling element holder | retainer, Comprising: (a) is a partial expansion perspective view of the 1st gear in the state which arranged the rolling element holding frame further. (B) is an AA cross-sectional view in (a).

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... 1st input shaft, 2 ... 2nd input shaft, 3 ... Output shaft, 4 ... Housing, 5 ... Bearing gear (rotating member), 6 ... Rotating shaft, 7 ... Rolling body holder, 11 ... Bearing, DESCRIPTION OF SYMBOLS 12 ... Bearing, 21 ... Inner peripheral surface, 22 ... Bearing, 23 ... Bearing, 51 ... Inner ring, 52 ... Outer ring, 53 ... Rolling element, 71 Connecting member, g1 ... First gear, g2 ... Second gear, g3 ... First 3 gears, g4 ... 4th gear, g11 ... concave groove, g12 ... rolling element, g13 ... inner diameter side holding frame, g14 ... outer diameter side holding frame, g21 ... concave groove, 71a ... connection portion, 71b ... connection portion, 72 ... groove, 72, 73 ... groove, 74, 75 ... claw, 76, 77 ... inclined structure, 81 ... recess, 101 ... first input shaft, 104 ... housing, 105 ... bearing gear, 111 ... bearing, 121 ... bearing , 151 ... inner ring, 152 ... outer ring, 153 ... rolling element, g101 ... first gear, g 02 ... 2nd gear, g103 ... 3rd gear, g104 ... 4th gear, g111 ... concave groove, g112 ... rolling element, g113 ... inner diameter side retainer, g114 ... outer diameter side retainer, g116 ... end, g117 ... End, g122 ... wall surface, g131 ... concave groove, g141 ... concave groove.

Claims (4)

The oscillating gear device includes a semi-cylindrical concave groove formed at equal intervals in the rotation direction, and a substantially cylindrical rolling element supported so as to be able to roll in the concave groove. A rolling element holder for holding the rolling element, which is used by being mounted on a gear that uses the moving element as convex teeth,
An inner diameter side holding frame that holds the rolling elements from the inside in the radial direction of the gear;
An outer diameter side holding frame that holds the rolling elements from the outside in the radial direction of the gear;
A connecting member for connecting the inner diameter side holding frame and the outer diameter side holding frame;
The inner diameter side holding frame and the outer diameter side holding frame have an arrangement structure for arranging the rolling elements at positions corresponding to the concave grooves,
The rolling element holder according to claim 1, wherein the connecting member has a detachable structure that can be detached from the inner diameter side holding frame and the outer diameter side holding frame in a state of being mounted on the gear.   2. The removal structure according to claim 1, wherein at least a part of the connection member is formed by reducing a shear strength as compared with the inner diameter side holding frame and the outer diameter side holding frame. Rolling element cage.     The rolling element holder according to claim 1, wherein the arrangement structure is a groove for inserting the rolling element.   The rolling element according to claim 1, wherein an inclined structure for guiding the rolling element into the groove is formed on the inner diameter side holding frame and the outer diameter side holding frame. Cage.

Images