JP2014081017A - Gear device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gear device capable of reducing the occurrence of skew and reducing the loss in a bearing.SOLUTION: A deflective meshing type gear device 100 has an outer teeth gear 120 supported via an excitation body bearing 110 on an outer circumference of the excitation body 104. Therein, the excitation body bearing 110 has rollers 116A, 116B and retainers 114A, 114B which retain the rollers 116A, 116B. The retainers 114A, 114B have retainer main bodies 114AA, 114BA which are provided with ring parts 114AAA, 114BAA arranged on axial direction O both sides and column parts 114AAB, 114BAB of connecting the ring parts 114AAA, 114BAA and are molded with resin, and metal ring bodies 114AB, 114BB fastened to the axial direction O outer sides of the ring parts 114AAA, 114BAA and the column parts 114AAB, 114BAB are not reinforced with metal.

Description

  The present invention relates to a gear device.

  Patent Document 1 includes a vibrator having a non-circular cross section, an external gear having flexibility that is bent and deformed by the rotation of the vibrator, and a rigidity with which the external gear meshes internally. A flexibly meshing gear device having an internal gear is disclosed. In this gear device, a bearing is disposed between the vibrator and the external gear. The bearing includes a plurality of rollers and a retainer that regulates the posture of the rollers.

JP 2011-158072 A

  However, as shown in Patent Document 1, using a roller in a gear device has an advantage that the load capacity can be increased as compared with the case of using a ball, but on the other hand, an excessive loss occurs in the bearing when skew occurs. Has the disadvantages.

  Accordingly, the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a gear device that can reduce the occurrence of skew and reduce the loss in the bearing.

  The present invention is a gear device having a gear supported on the outer periphery of a shaft via a bearing, the roller having a roller and a retainer for holding the roller, and the retainer having both sides in the axial direction. A retainer main body formed of a resin including a ring portion disposed on the ring portion and a column portion connecting the ring portion, and a metal ring member fixed to the axially outer side of at least one of the ring portions. And the said subject is solved because the said pillar part is not reinforced by the metal.

  That is, in the present invention, a metal ring member is fixed to the outside in the axial direction of at least one ring portion of the retainer main body formed of resin. For this reason, the rigidity of the entire retainer can be improved while reducing friction loss with the retainer main body. Here, in the present invention, the ring portion is reinforced with metal, whereas the column portion is not reinforced with metal. For this reason, when the local contact load with the retainer place which arises when it is going to generate | occur | produce a skew without being able to regulate skew, a pillar part becomes a structure which is easy to deform | transform compared with a ring part compared with a ring part. That is, according to the present invention, even if a local force is applied to the retainer when the skew occurs, the local force can be relaxed there by positively deforming the column portion. For this reason, the improvement from the original shape of a retainer can be avoided combined with the improvement of the rigidity of the whole retainer by a metal ring member. That is, since the retainer is prevented from being deformed, as a result, the retainer can stably regulate the posture of the roller.

  According to the present invention, it is possible to reduce the occurrence of skew and the loss in the bearing.

The perspective view which shows an example of the whole structure of the bending meshing gear apparatus which concerns on 1st Embodiment of this invention. Sectional view including the axis of FIG. Sectional view along line III-III in FIG. Schematic side view of the vibrator bearing retainer from the circumferential direction Sectional drawing (A) of the vibration body bearing which concerns on 1st Embodiment of this invention, and Cross-sectional view (B) of the vibration body bearing which concerns on 2nd Embodiment Sectional drawing (A) which shows an example of a structure centering on the bearing of the gear apparatus which concerns on 3rd Embodiment of this invention, and the enlarged view (B) of the bearing

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

  First, the overall configuration of the present embodiment will be schematically described with reference to FIGS.

  The flexure meshing gear device 100 (gear device) is arranged on the outer periphery of the vibration generating body 104 (shaft) and the vibration generating body 104 and has a flexible outer shape that is bent and deformed by the rotation of the vibration generating body 104. A tooth gear 120 (gear), a reduction internal gear 130A having a rigidity with which the external gear 120 meshes internally, an output internal gear 130B (internal gear 130), an oscillator 104 and an external gear And a vibration body bearing 110 (bearing) disposed between the two and 120. That is, the flexure meshing gear device 100 includes external gears 120 (120A, 120B) supported on the outer periphery of the vibration generator 104 via the vibration generator bearing 110. Here, the vibration body bearing 110 includes rollers 116A and 116B and retainers 114A and 114B that hold the rollers 116A and 116B. The retainers 114A and 114B include retainer main bodies 114AA and 114BA and metal ring bodies 114AB and 114BB (metal ring members). The retainer main bodies 114AA and 114BA include two ring portions 114AAA and 114BAA arranged at both ends in the axial direction O, and pillar portions 114AAB and 114BAB that connect the ring portions 114AAA and 114BAA. The metal ring bodies 114AB and 114BB are fixed to the outer side in the axial direction O of the ring portions 114AAA and 114BAA. Note that the pillars 114AAB and 114BAB are not reinforced with metal.

  Hereinafter, each component will be described in detail.

  As shown in FIGS. 1 to 3, the vibration body 104 has a substantially columnar shape with a non-circular cross section, and realizes a meshing state between the external gear 120 and the internal gear 130 in the major axis direction X, and the short body The non-meshing state of the external gear 120 and the internal gear 130 is realized in the axial direction Y. More specifically, the vibrating body 104 has a meshing range of an outer shape with a constant curvature radius r1 centered on an eccentric position (an eccentric amount L), and has a shape in which a plurality of curvature radii are combined. The vibrator 104 is formed with an input shaft hole 106 into which an input shaft (not shown) is inserted at the center. A keyway 108 is provided in the input shaft hole 106 so that the vibrator 104 rotates integrally with the input shaft when the input shaft is inserted and rotated.

  As shown in FIG. 1, two vibration body bearings 110 (110A, 110B) are arranged side by side in the axial direction O. The vibration body bearing 110 is a bearing disposed between the outer periphery of the vibration body 104 and the inside of the external gear 120. The vibration body bearings 110A and 110B have the same configuration, and the inner ring 112 is common to both. For this reason, below, the vibration body bearing 110A is demonstrated and description about the vibration body bearing 110B is abbreviate | omitted.

  As shown in FIGS. 1, 2, and 5A, the vibration body bearing 110A includes an inner ring 112, a retainer 114A, a roller 116A as a rolling element, and an outer ring 118A.

  The inner ring 112 is made of a flexible material. The inner ring 112 is disposed on the side of the vibration generator, the inner peripheral surface of the inner ring 112 is in contact with the vibration generator 104, and the inner ring 112 rotates integrally with the vibration generator 104.

  The retainer 114A includes a retainer main body 114AA, a metal ring body 114AB, and a resin film 114AC, as shown in FIGS. The retainer main body 114AA is a member having a pair of ring portions 114AAA, column portions 114AAB, and pockets 114AAC, all of which are formed of resin. The pair of ring portions 114AAA are connected by a plurality of column portions 114AAB protruding in the axial direction O. A plurality of column portions 114AAB are arranged at equal intervals in the circumferential direction of the retainer 114A. That is, the column portion 114AAB accommodates the roller 116A between the column portions 114AAB (pocket 114AAC) and regulates the position and posture of the roller 116A in the circumferential direction. A metal ring body 114AB is fixed (by sticking or integral molding) on the outer side in the axial direction O of the ring portion 114AAA. The metal ring body 114AB is a metal ring-shaped member, and its radial direction R thickness is substantially the same as that of the retainer body 114AA. The pair of ring portions 114AAA are reinforced by the metal ring body 114AB. On the other hand, the pillar portion 114AAB is not in a form reinforced with metal.

  In this embodiment, as shown in FIGS. 2 and 5A, the vibration body bearing 110A is arranged side by side with the vibration body bearing 110B in the axial direction O, and the metal ring bodies 114AB and 114BB are in contact with each other. The positions are mutually regulated. For this reason, the retainer 114A is positioned in the axial direction O by adjusting the thickness in the axial direction O of the metal ring body 114AB. A resin film 114AC is formed on the outer surface in the axial direction O of the metal ring body 114AB. The resin film 114AC is made of a resin having a low friction coefficient and a high slidability. The resin film 114AC may be formed by coating the metal ring body 114AB, or by attaching a thin ring-shaped resin plate. Also good. The resin film 114AC is provided as a friction reducing process on the outer surface in the axial direction O of the metal ring body 114AB, and improves the lubrication of the lubricating oil sealed in the gear device, not the resin films 114AC and 114BC. Alternatively, a surface treatment (such as a dimple treatment) on which an oil film is easily formed may be provided instead. In addition, this low friction process is not necessarily a required structure.

  The roller 116A has a cylindrical shape (including a needle shape) as shown in FIGS. 2, 3, and 5A. For this reason, compared with the case where a rolling element is a ball | bowl, the part which the roller 116A contacts with the inner ring | wheel 112 and the outer ring | wheel 118A is increased. That is, by using the rollers 116A, the transmission torque of the vibration body bearing 110A can be increased and the life can be extended.

  As shown in FIGS. 2, 3, and 5A, the outer ring 118A is disposed on the outer periphery of the roller 116A and the retainer 114A. The outer ring 118A is also formed of a flexible material. The outer ring 118 </ b> A is bent and deformed by the rotation of the vibration generator 104 together with the external gear 120 </ b> A disposed on the outer periphery thereof.

  As shown in FIGS. 1 and 2, the external gear 120 </ b> A meshes internally with a reduction internal gear 130 </ b> A. The external gear 120A includes a base member 122 and external teeth 124A. The base member 122 is a flexible cylindrical member that supports the external teeth 124 </ b> A, and is disposed outside the vibration body bearing 110. The tooth profile of the external tooth 124A is determined based on the trochoid curve so as to realize theoretical meshing.

  As shown in FIGS. 1 and 2, the external gear 120B meshes internally with the output internal gear 130B. And the external gear 120B is comprised from the base member 122 and the external tooth 124B similarly to the external gear 120A. The external teeth 124B are configured in the same number and shape as the external teeth 124A. Here, the base member 122 supports the external teeth 124A and the external teeth 124B in common. For this reason, the eccentric amount L of the vibrator 104 is transmitted to the external teeth 124A and the external teeth 124B in the same phase.

  As shown in FIGS. 1 and 2, the reduction internal gear 130A and the output internal gear 130B are arranged side by side in the axial direction O corresponding to the vibration body bearings 110A and 110B. The reduction internal gear 130A is formed of a rigid member. The reduction internal gear 130A includes internal teeth 128A whose number of teeth is i (i is 2 or more) greater than the number of external teeth 124A of the external gear 120A. The inner teeth 128A are shaped to theoretically mesh with the outer teeth 124A based on the trochoid curve (the inner teeth 128B are also the same). The internal gear 130A for deceleration reduces the rotation of the vibration generator 104 by meshing with the external gear 120A. The internal gear 130A for deceleration is fixed to a fixed wall (not shown) via a bolt hole 132A, for example.

  On the other hand, the output internal gear 130B is also formed of a rigid member, like the reduction internal gear 130A. The output internal gear 130B includes internal teeth 128B having the same number of teeth as the external teeth 124B of the external gear 120B. From the output internal gear 130B, the same rotation as the rotation of the external gear 120B is output to the outside. The output internal gear 130B is fixed to an output device (not shown) through a bolt hole 132B, for example.

  Next, the operation of the flexibly meshing gear device 100 will be described mainly with reference to FIGS.

  When the vibration generator 104 is rotated by rotation of an input shaft (not shown), the external gear 120A is bent and deformed via the vibration generator bearing 110A according to the rotation state. At this time, the external gear 120B is also bent and deformed in the same phase as the external gear 120A via the vibration body bearing 110B.

  When the external gears 120A and 120B are bent and deformed by the vibrating body 104, the external teeth 124A of the external gear 120A mesh with the internal teeth 128A of the reduction internal gear 130A within the meshing range. Similarly, the external teeth 124B of the external gear 120B mesh with the internal teeth 128B of the output internal gear 130B.

  At this time, since the rollers 116A and 116B of the vibration body bearings 110A and 110B have a cylindrical shape, the load resistance is large, and the life of the vibration body bearings 110A and 110B can be extended and the transmission torque can be improved. At the same time, the cylindrical rollers 116A and 116B bend and deform the base member 122 of the external gears 120A and 120B in parallel to the axial direction O. For this reason, the vibration body bearings 110A and 110B extend the life of the outer teeth 124A and 124B and the inner teeth 128A and 128B, and maintain high torque transmission.

  Here, the external teeth 124A and 124B are divided in the axial direction O into a portion where the internal gear 130A for reduction is engaged and a portion where the output internal gear 130B is engaged. Therefore, when the external gear 120A and the reduction internal gear 130A mesh with each other, the meshing area that the external teeth 124A and the internal teeth 128A should mesh with each other in the axial direction O is not affected by the external teeth 124B. Engage with. Similarly, when the external gear 120B meshes with the output internal gear 130B, the meshing area that the external teeth 124B and the internal teeth 128B should originally mesh in the axial direction O without being affected by the external teeth 124A. Engage with. That is, by dividing the external teeth 124A and 124B, it is possible to prevent a decrease in transmission torque.

  The meshing position of the external gear 120 </ b> A and the reduction internal gear 130 </ b> A rotates as the vibration body 104 moves in the long axis direction X. Here, when the vibrating body 104 rotates once, the rotation phase of the external gear 120A is delayed by a difference in the number of teeth from the internal gear 130A for deceleration. That is, the reduction ratio by the internal gear 130A for reduction can be obtained by ((number of teeth of external gear 120A−number of teeth of internal gear 130A for reduction) / number of teeth of external gear 120A). The specific reduction ratio is ((100−102) / 100 = −1 / 50). Here, “−” indicates that the input / output is in a reverse rotation relationship.

  Since both the external gear 120B and the output internal gear 130B have the same number of teeth, the external gear 120B and the output internal gear 130B do not move with each other, and the same teeth can move. Will be engaged. For this reason, the same rotation as the rotation of the external gear 120B is output from the output internal gear 130B. As a result, an output obtained by reducing the rotation of the vibrating body 104 to (−1/50) can be extracted from the output internal gear 130B.

  In the present embodiment, metal ring bodies 114AB and 114BB are fixed to the outer side in the axial direction O of the ring portions 114AAA and 114BAA of the retainer main bodies 114AA and 114BA formed of resin. For this reason, the rigidity of the retainers 114A and 114B as a whole can be improved while reducing friction loss with the retainer main bodies 114AA and 114BA, that is, 116A and 116B. Here, in this embodiment, the ring portions 114AAA and 114BAA are reinforced with metal, whereas the column portions 114AAB and 114BAB are not reinforced with metal. For this reason, when the local contact load with the retainers 114A and 114B and the retainers 114A and 114B, which is generated when the skew is generated without being able to regulate the skew, the column is compared with the ring portions 114AAA and 114BAA when the retainers 114A and 114B are subjected to local contact load. The parts 114AAB and 114BAB are easily deformed. That is, in this embodiment, even if a local force is applied to the retainers 114A and 114B when a skew occurs, the local forces are relieved by positively deforming the column portions 114AAB and 114BAB. be able to. For this reason, coupled with the improvement of the rigidity of the retainers 114A and 114B by the metal ring bodies 114AB and 114BB, the deformation of the retainers 114A and 114B from the original shape can be avoided. That is, even when a local force is received from the rollers 116A and 116B, the retainers 114A and 114B are prevented from being deformed. And the movement from the position of the original axial direction O of retainer 114A, 114B can also be avoided simultaneously by the effect of the said relaxation. Therefore, as a result, the retainers 114A and 114B can stably regulate the postures of the rollers 116A and 116B.

  In addition, when the pillar part is reinforced with metal (or the pillar part is metal itself), the pillar part cannot be locally deformed and it is difficult to release (relax) the contact load. In that case, there is a possibility that the vibration generator bearing may be locked or skewed.

  In the present embodiment, the vibration body bearings 110A and 110B, except for the inner ring 112, in the axial direction O and the portion corresponding to the external teeth 124A meshing with the reduction internal gear 130A and the output internal gear 130B It is separated into a portion for meshing external teeth 124B. For this reason, even when different forces (direction and size) are applied to the external teeth 124A and the external teeth 124B during meshing, the skew of the rollers 116B caused by the meshing between the internal gear 130A for deceleration and the external teeth 124A, Each of the skews of the rollers 116A caused by the meshing between the output internal gear 130B and the external teeth 124B is less likely to occur.

  And in this embodiment, vibration body bearing 110A, 110B is arrange | positioned along with the axial direction O, metal ring body 114AB, 114BB contact | abuts and mutually positions-regulate (In this embodiment, it is actually contacting. The resin films 114AC and 114BC for reducing the friction, however, in the present invention, the resin films 114AC and 114BC are actually captured by taking the metal ring member including the film for reducing the friction. Even if they are in contact with each other, it is included in the concept that metal ring members are in contact with each other). For this reason, the adjustment member for adjusting the position of vibration body bearing 110A, 110B can be made unnecessary. At the same time, since the axial thickness O of the metal ring bodies 114AB and 114BB is configured by adding the axial thickness O of the adjusting member, the rigidity of the retainers 114A and 114B as a whole can be further improved. That is, also from this viewpoint, the retainers 114A and 114B can be prevented from being deformed, and the original shapes of the retainers 114A and 114B can be maintained. Furthermore, since the retainers 114A and 114B are prevented from being deformed, the skew is reduced and the thrust force applied to the retainers 114A and 114B is reduced. For this reason, even if metal ring body 114AB and 114BB contact | abut, friction loss there can be reduced.

  In addition, in the present embodiment, resin films 114AC and 114BC are provided on the outer surfaces in the axial direction O of the metal ring bodies 114AB and 114BB. For this reason, even if metal ring body 114AB and 114BB contact | abut, it is possible to further reduce the friction loss there. The resin films 114AC and 114BC are also formed on the outer surface in the axial direction O of the metal ring bodies 114AB and 114BB toward the outside of the flexure meshing gear device 100, as shown in FIGS. . For this reason, even if a member such as a fixed wall or an output device arranged on the side of the vibration body bearing 110 comes into contact with the metal ring bodies 114AB and 114BB, it is possible to reduce the friction loss.

  Therefore, in this embodiment, even if the rollers 116A and 116B are used as the rolling elements, the protrusion of the vibration generator bearing 110 in the axial direction O from the vibration generator 104 due to the skew, and the rollers 116A and 116B It is possible to prevent an increase in rolling resistance (including lock) and a decrease in torque transmission efficiency. In other words, according to the present embodiment, it is possible to reduce the loss in the vibration body bearing 110 by reducing the occurrence of skew.

  Although the present invention has been described with reference to the first embodiment, the present invention is not limited to the first embodiment. That is, it goes without saying that improvements and design changes can be made without departing from the scope of the present invention.

  For example, in the first embodiment, as shown in FIG. 5A, the vibration body bearings 110A and 110B are arranged side by side in the axial direction O, and the metal ring bodies 114AB and 114BB are in contact with each other to regulate their positions. However, the present invention is not limited to this. For example, as in the second embodiment shown in FIG. 5B, an adjusting member 219 for adjusting the respective positions may be arranged between the vibrator bearings 210A and 210B. Since the configuration other than the adjustment member 219 is the same as that of the first embodiment, the description other than the adjustment member 219 is omitted with the same last two digits being the same.

  In this case, since the axial direction O thickness of the adjusting member 219 can be adjusted independently of the metal ring bodies 214AB and 214BB, the position of the vibration body bearing 210 in the axial direction O can be easily adjusted.

  In the above embodiment, the vibration body bearing has an inner ring, a retainer, a roller, and an outer ring. However, the present invention is not limited to this, and the vibration body bearing does not necessarily include the inner ring, the retainer, the roller, and the outer ring. There is no need to have. For example, the inner ring may be integrated with the vibration generating body without an inner ring, and the outer peripheral portion of the vibration generating body may be an inner ring member. The inner peripheral portion of the gear may be an outer ring member.

  Moreover, in the said embodiment, although the external tooth was made into the tooth profile based on the trochoid curve, this invention is not limited to this. The external teeth may be arc teeth or other teeth.

  Moreover, in the said embodiment, although the output decelerated from the internal gear for output was taken out, this invention is not limited to this. For example, a so-called cup-type in which a vibration body bearing having a roller and an external gear are each provided, and a side portion on one side in the axial direction O of the external gear is released without using an internal gear for output. As an external gear that bends and deforms, the external gear may be applied to a flexure meshing gear device that directly extracts only its rotation component from the other side in the axial direction O of the external gear.

  Further, in the above embodiment, the metal ring body has only the same radial direction R thickness as the retainer main body, but the present invention is not limited to this, for example, as shown in the third embodiment shown in FIG. It may be in the form of a metal ring. Since the configuration of the retainer main body 314AA and 316A is the same as that of the above embodiment, the description of the retainer main body 314AA and the rollers 316A is the same with the last two digits of the reference numerals, and redundant description is omitted.

  In the third embodiment, as shown in FIG. 6A, for example, the gear device 300 includes a rotary shaft 304 (shaft) integrally including an eccentric body 305A, and an eccentric body bearing 310A (bearing) on the outer periphery of the eccentric body 305A. The external gear 320A (gear) is supported via the. The rotating shaft 304 is rotatably supported by the main bearing 340. The external gear 320A is configured to swing and rotate according to the shape of the eccentric body 305A via the eccentric body bearing 310A.

  As shown in FIG. 6B, the retainer 314A has a retainer main body 314AA, a metal ring body 314AB, and a resin film 314AC. A metal ring body 314AB is fixed to the outside in the axial direction O of the ring portion 314AAA. One of the metal ring bodies 314AB is provided with an extending portion 314ABA extending inward in the radial direction R of the eccentric body bearing 310A with respect to the ring portion 314AAA. And resin film 314AC is shape | molded on the both sides | surfaces of the axial direction O of extension part 314ABA. A resin film 314AC is also formed on the other outer surface in the axial direction O of the metal ring body 314AB in order to reduce friction loss when coming into contact with the retainers arranged in parallel. As shown in FIG. 6A, the extending portion 314ABA is disposed so as to be sandwiched between the side surface of the eccentric body 305A and the side surface of the main bearing 340. That is, the extending portion 314ABA is sandwiched between two members, the eccentric body 305A and the main bearing 340, so that the position of the metal ring body 314AB is restricted in the axial direction O.

  Therefore, in the third embodiment, the positioning of the eccentric body bearing 310A in the axial direction O can be stricter due to the metal ring body 314AB, and the axial direction of the retainer 314A can be prevented in combination with the prevention of deformation of the retainer 314A by improving the rigidity of the retainer 314A. The movement to O can be restricted. At the same time, the deformation of the retainer 314A is prevented, thereby reducing the skew and reducing the thrust force applied to the retainer 314A. For this reason, even if metal ring body 314AB contact | abuts with the main bearing 340 and the eccentric body 305A, the friction loss there can be reduced. In addition, since the resin film 314AC is formed on both surfaces of the extending portion 314ABA as a friction reducing process, the friction loss can be reduced even if it contacts the main bearing 340 and the eccentric body 305A. That is, in the third embodiment, it is possible to further reduce the occurrence of skew and reduce the loss in the eccentric body bearing 310A.

  In the third embodiment, the object is a gear device having an external gear that oscillates and rotates. Of course, the object is the flexure meshing gear device shown in the first and second embodiments. Also good. In addition, the resin film 314AC in the third embodiment is an example of a friction reduction process, and is not limited to the resin film 314AC as described in the above embodiment, and the friction reduction process is not necessarily required.

  In the above embodiment, the metal ring body is fixed to the outside of both the axial directions O of the ring portions arranged on both sides of the axial direction O. However, the present invention is not limited to this, and the metal ring body is at least one of the metal ring bodies. What is necessary is just to adhere to the axial direction O outer side of a ring part. With such a configuration, it becomes possible to improve the rigidity of the retainer accordingly.

  In the above embodiment, the present invention is applied to a flexure meshing gear device and an eccentric oscillating gear device in which an external gear oscillates. However, the present invention is not limited to these applications. However, the present invention can be applied to a gear device having a gear widely supported through a bearing having rollers on the outer periphery of the shaft. For example, the present invention can be applied to a simple planetary gear device including a sun gear and a planetary gear arranged around the sun gear. Furthermore, the present invention can be applied to a more general ordinary parallel shaft gear device, a straight shaft gear device, or the like. Similarly, an effect of reducing a skew and reducing a loss in a bearing can be obtained.

  The present invention is widely applicable to a gear device having a gear supported on the outer periphery of a shaft via a bearing, the bearing having a retainer for regulating the posture of the roller.

DESCRIPTION OF SYMBOLS 100 ... Flexure-meshing type gear apparatus 104 ... Excitation body 110,110A, 110B, 210,210A, 210B ... Excitation body bearing 112,212 ... Inner ring 114A, 114B, 214A, 214B, 314A ... Retainer 114AA, 114BA, 214AA , 214BA, 314AA ... Retainer main body 114AAA, 114BAA, 314AAA ... Retainer ring 114AAB, 114BAB ... Retainer pillar 114AAC ... Retainer pocket 114AB, 114BB, 214AB, 214BB, 314AB ... Metal ring body 114AC, 114BC, 214AC, 214B 314AC: Resin film 116A, 116B, 216A, 216B, 316A ... Roller 118A, 118B, 218A, 218B ... Outer ring 120, 120A, 120B, 3 20A ... external gear 122 ... base member 124, 124A, 124B ... external tooth 128, 128A, 128B ... internal tooth 130, 130A ... internal gear for reduction (internal gear)
130B: Internal gear for output 219 ... Adjustment member 300 ... Gear device 304 ... Rotating shaft 305A ... Eccentric body 310A ... Eccentric body bearing 314ABA ... Extension part 340 ... Main bearing O ... Axial direction R ... Radial direction X ... Exciter Long axis direction Y ... Short axis direction of the vibrator

Claims (5)

A gear device having a gear supported on the outer periphery of a shaft via a bearing,
The bearing has a roller and a retainer that holds the roller,
The retainer includes a retainer body formed of a resin including a ring portion disposed on both sides in the axial direction and a column portion that connects the ring portion, and a metal that is fixed to the outside in the axial direction of at least one of the ring portions. A ring member,
The said pillar part is not reinforced with metal. The gear apparatus characterized by the above-mentioned. In claim 1,
Two of the bearings are arranged side by side in the axial direction, and the ring members made of metal are in contact with each other and their positions are regulated. In claim 1 or 2,
The shaft is a vibrator having a non-circular cross section, the gear is a flexible external gear that is bent and deformed by the rotation of the vibrator, and the external gear is in mesh with the internal gear. An internal gear having
The bearings are arranged side by side in the axial direction,
Two of the internal gears are arranged side by side in the axial direction corresponding to the bearing. In any one of Claims 1 thru | or 3,
A gear device characterized in that a low friction treatment is applied to an axially outer side surface of the metal ring member. In any one of Claims 1 thru | or 4,
The gear ring device is characterized in that the metal ring member extends radially inward of the bearing from the ring portion and is positioned by being sandwiched between two members.

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