JP2019011795A - Speed reducer - Google Patents

Abstract

To provide a speed reducer capable of actualizing a smaller size and higher durability while developing a high output and also avoiding the lowering of operation stability and driving force transmission efficiency in connection with the interference of one member with the other.SOLUTION: The speed reducer includes a casing 2, a fixed internal gear 3 fixed to the casing 2, a movable internal gear 4 supported rotatably relative to the casing 2, an input shaft 5 having an eccentric part 5a on the outer peripheral face, a bearing member 10 arranged on the outer periphery of the eccentric part 5a, first rollers 6 arranged between the fixed internal gear 3 and the bearing member 10, second rollers 7 arranged between the movable internal gear 4 and the bearing member 10, and a holder 8 rotatably holding the rollers 6, 7. The bearing member 10 is arranged on the inner periphery of the holder 8. The holder 8 is rotatably guided with the help of the outer peripheral face of the bearing member 10.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a reduction gear.

  Conventionally, as a reduction gear mounted on vehicles, industrial robots, etc., a roller is sequentially engaged with a plurality of teeth formed on the inner peripheral surface of an internal gear, and the rotation of the input shaft is decelerated and transmitted to the output shaft. A roller-type speed reducer is known.

  In general, this type of reduction gear includes an input shaft 100 having an eccentric portion 100a on the outer peripheral surface, an internal gear 200 having a plurality of teeth formed on the inner peripheral surface, and an internal gear, as in the example shown in FIG. 200, a plurality of rollers 300 disposed between the inner peripheral surface of the input shaft 100 and the eccentric portion 100a of the input shaft 100, a holder 400 that rotatably holds the roller 300, and an output shaft that is configured integrally with the holder 400. 500 (see Patent Document 1). When a driving force is input to the input shaft 100 from a driving source such as an electric motor and the input shaft 100 is rotated, the roller 300 is sequentially engaged with the teeth of the internal gear 200 by the rotation of the eccentric portion 100a. As the roller 300 moves by one tooth in the circumferential direction for every rotation, the output shaft 500 rotates at a reduced speed with respect to the input shaft 100.

JP 62-93565 A

  In recent years, a roller-type speed reducer as described above has been demanded to have a small size while having a high reduction ratio and high output. In response to such a request, as one method for realizing high output, it is conceivable to increase the reduction gear ratio by increasing the number of teeth of the internal gear. However, when the number of teeth of the internal gear is increased, the radial size of the internal gear is increased, which is against the demand for downsizing.

  Further, in the configuration as shown in FIG. 10, since the cage also functions as an output rotating body that rotates by receiving the force from the roller, in order to obtain a high torque by increasing the reduction ratio, There exists a subject that the intensity | strength which a cage | basket can endure high torque must be ensured. However, since the cage cannot be significantly increased in thickness due to its function, it is difficult to ensure strength against torque increase. Therefore, it has been difficult to sufficiently respond to the demand for higher output with the conventional configuration.

  Under such circumstances, development of a new roller-type speed reducer that is different from the conventional one is required, but when developing a new roller-type speed reducer, there is a possibility that relatively rotating members may interfere with each other. This leads to malfunctions and reduced drive transmission efficiency. For this reason, in the development of a new roller-type speed reducer, it has been an important issue to improve reliability by reliably preventing interference between members.

  Therefore, the present invention provides a reduction gear capable of realizing a reduction in size and an improvement in durability while having a high output, and further avoiding a decrease in operational stability and a decrease in driving force transmission efficiency due to interference between members. For the purpose.

  As technical means for achieving the above-mentioned object, the present invention includes a casing, a fixed internal gear fixed to the casing and provided with a plurality of teeth on the inner peripheral surface, and rotatably supported with respect to the casing. A movable internal gear provided with a plurality of teeth on the inner peripheral surface, an input shaft having an eccentric portion eccentric to the fixed internal gear and the movable internal gear on the outer peripheral surface, and a bearing member disposed on the outer periphery of the eccentric portion A plurality of first rollers disposed between the inner peripheral surface of the fixed internal gear and the bearing member; a plurality of second rollers disposed between the inner peripheral surface of the movable internal gear and the bearing member; A holder that rotatably holds the first roller and the second roller, and each time the input shaft makes one rotation, the first roller moves in the circumferential direction by one tooth of the fixed internal gear, and the second roller Moves in the circumferential direction by one tooth of the movable internal gear, so that the movable internal gear A speed reducer that decelerates and rotates with respect to a force shaft, wherein the bearing member is disposed on the inner periphery of the cage, and is configured to guide the cage rotatably by the outer peripheral surface of the bearing member. To do.

  In the speed reducer according to the present invention, each time the input shaft rotates once, the first roller moves in the circumferential direction by one tooth of the fixed internal gear, so that the cage rotates at a reduced speed with respect to the input shaft. Further, as the cage is decelerated, the second roller moves in the circumferential direction by one tooth of the movable internal gear for each rotation of the input shaft, so that the movable internal gear rotates at a reduced speed with respect to the input shaft. . As described above, by reducing the speed between the fixed internal gear and the first roller and between the movable internal gear and the second roller and transmitting the rotation, the number of teeth of the internal gear can be reduced in the conventional speed reducer. Compared to measures to increase the power output by increasing the number, it is possible to provide a small speed reducer with high output.

  In the speed reducer according to the present invention, since the movable internal gear functions as an output rotator, it becomes easier to ensure rigidity compared to the conventional configuration in which the cage is the output rotator. That is, the movable internal gear has a degree of freedom in the radial direction as compared with the cage and can be formed thick, so that it can sufficiently cope with an increase in torque associated with higher output.

  Furthermore, in the speed reducer according to the present invention, the cage can be rotatably rotated by the outer peripheral surface of the bearing member to prevent the cage from swinging in the radial direction (movement in the radial direction). As a result, it is possible to reliably prevent the cage from interfering with the fixed internal gear or the movable internal gear, and to avoid malfunctions and reduction in driving force transmission efficiency due to these interferences. In addition, by preventing the cage from swinging in the radial direction, it is possible to prevent the first roller or the second roller from being caught due to a narrow interval between the cage and the fixed internal gear or the movable internal gear. And reliability is improved.

  For example, the cage can be guided by the outer circumferential surface of the bearing member by directly contacting the inner circumferential surface of the cage with the outer circumferential surface of the bearing member.

  Further, an annular member may be disposed between the inner peripheral surface of the cage and the outer peripheral surface of the bearing member, and the cage may be brought into contact with the outer peripheral surface of the bearing member via the annular member.

  For example, the annular member is disposed between a pocket of the cage in which the first roller is accommodated and a pocket of the cage in which the second roller is accommodated. Moreover, an annular member may be arrange | positioned at the axial direction both ends of a holder | retainer.

  Since the annular member functions as a slide bearing, the cage can be smoothly rotated via the annular member.

  The annular member is preferably formed of a resin material having slidability.

  According to the present invention, it is possible to improve the miniaturization and durability while maintaining a high output, and further, it is possible to avoid a decrease in operational stability and a decrease in driving force transmission efficiency due to interference between members.

It is a longitudinal section of a reduction gear concerning one embodiment of the present invention. It is a disassembled perspective view of the reduction gear shown in FIG. It is an AA arrow directional cross-sectional view in FIG. It is a BB sectional view taken on the line in FIG. It is a longitudinal cross-sectional view of the reduction gear which concerns on other embodiment of this invention. It is a disassembled perspective view of the reduction gear shown in FIG. It is CC sectional view taken on the line in FIG. It is a longitudinal cross-sectional view of the reduction gear which concerns on another embodiment of this invention. It is a disassembled perspective view of the reduction gear shown in FIG. It is a longitudinal cross-sectional view of the conventional reduction gear.

  Hereinafter, the present invention will be described with reference to the accompanying drawings. In the drawings for explaining the present invention, components such as members and components having the same function or shape are denoted by the same reference numerals as much as possible, and once described, the description will be given. Omitted.

  FIG. 1 is a longitudinal sectional view of a reduction gear according to an embodiment of the present invention, and FIG. 2 is an exploded perspective view of the reduction gear shown in FIG. 3 is a cross-sectional view taken along line AA in FIG. 1, and FIG. 4 is a cross-sectional view taken along line BB in FIG.

  As shown in FIGS. 1 to 4, the speed reducer 1 according to the present embodiment includes a casing 2, a fixed internal gear 3 fixed to the casing 2, and a movable internal gear supported rotatably with respect to the casing 2. 4, the input shaft 5 having the eccentric portion 5 a on the outer peripheral surface, the plurality of first rollers 6 disposed between the inner peripheral surface of the fixed internal gear 3 and the eccentric portion 5 a, and the inner periphery of the movable internal gear 4 A plurality of second rollers 7 disposed between the surface and the eccentric portion 5a and a cage 8 that rotatably holds the first roller 6 and the second roller 7 are mainly configured.

  The casing 2 is formed in a cylindrical shape. A radial step surface 2a (see FIG. 1) is formed in the middle of the inner peripheral surface of the casing 2 in the axial direction. A small inner diameter having a small inner diameter on one side in the axial direction with the step surface 2a as a boundary. A portion 2c is formed, and a large inner diameter portion 2d having a larger inner diameter than the small inner diameter portion 2c is formed on the other side in the axial direction.

  The fixed internal gear 3 is an annular gear member having a plurality of teeth 3a formed on the inner peripheral surface. The plurality of teeth 3a are arranged at equal intervals in the circumferential direction of the fixed internal gear 3, and a curved tooth groove 3c (see FIG. 3) is formed between the teeth 3a. The fixed internal gear 3 is provided with a plurality of holes 3b at equal intervals in the circumferential direction. The projection 2b provided on the stepped surface 2a of the casing 2 is fitted into these holes 3b, so that the fixed internal gear 3 is fixed so as not to rotate on the inner periphery of the large inner diameter portion 2d of the casing 2. Yes. The fixed internal gear 3 may be integrally formed on the inner surface of the casing 2.

  The movable internal gear 4 is an annular gear member that has a plurality of teeth 4 a on the inner peripheral surface and is formed to have substantially the same outer diameter and inner diameter as the fixed internal gear 3. The plurality of teeth 4a are formed at equal intervals in the circumferential direction of the movable internal gear 4, and curved tooth grooves 4c (see FIG. 4) are formed between the teeth 4a. The number of teeth of the movable internal gear 4 is set to a number different from the number of teeth of the fixed internal gear 3. The movable internal gear 4 is arranged on the inner periphery of the large inner diameter portion 2d of the casing 2 adjacent to the fixed internal gear 3 in the axial direction (on the opening side of the casing 2), and the inner peripheral surface of the large inner diameter portion 2d. It is supported so as to be able to rotate by sliding with respect to. Further, the movable internal gear 4 is provided with a plurality of holes 4b at equal intervals in the circumferential direction. The output side member can be fixed to the movable internal gear 4 by fitting convex portions provided on the output side member (not shown) into these holes 4b. The movable internal gear 4 may be formed integrally with an output side member (not shown).

  The input shaft 5 is a cylindrical member to which driving force is input from a driving source (not shown) such as an electric motor. An eccentric portion 5 a having an outer peripheral surface that is eccentric in the radial direction by a distance Y with respect to the central axis (rotating shaft) of the input shaft 5 is provided at an intermediate portion in the axial direction of the input shaft 5. The eccentric portion 5 a is formed so as to protrude in the radial direction from the other portions of the input shaft 5, and is located on the inner circumferences of the fixed internal gear 3 and the movable internal gear 4.

  Two rolling bearings 10 and 11 as bearing members are arranged on the outer periphery of the input shaft 5. One rolling bearing 10 is an eccentric bearing that is press-fitted into the outer peripheral surface of the eccentric portion 5 a and is eccentric with respect to the central axis of the input shaft 5. The first roller 6 and the second roller 7 are disposed between the rolling bearing 10 and the inner peripheral surface of the fixed internal gear 3 or the inner peripheral surface of the movable internal gear 4, and roll on the outer peripheral surface of the rolling bearing 10. It is configured to be possible. The other rolling bearing 11 is press-fitted between the outer peripheral surface on one end side of the input shaft 5 and the small inner diameter portion 2 c of the casing 2, and the input shaft 5 can be rotated with respect to the casing 2 by the rolling bearing 11. It is supported by.

  The cage 8 is a cylindrical member, and is rotatably disposed between the rolling bearing 10 press-fitted into the eccentric portion 5 a and the internal gears 3 and 4. In the cage 8, a plurality of pockets 8a and 8b arranged at equal intervals in the circumferential direction are formed in two rows in the axial direction. One row of pockets (first pockets) 8a contains one first roller 6, and the other row of pockets (second pockets) 8b contains one second roller 7. Yes. The rollers 6 and 7 are held so as to be movable in the radial direction in the pockets 8a and 8b.

  Here, since the rolling bearing (eccentric bearing) 10 press-fitted into the outer peripheral surface of the eccentric portion 5a is eccentric with respect to the central axis of the input shaft 5, as shown in FIG. 3 and FIG. The centers Q1 and Q2 of the circles passing through the central axes of the first roller 6 and the second roller 7 arranged on the outer peripheral surface 10 are also eccentric in the radial direction Y with respect to the central axis O of the input shaft 5. On the other hand, the central axes of the fixed internal gear 3 and the movable internal gear 4 are arranged coaxially with the central axis O of the input shaft 5. For this reason, the centers Q1 and Q2 of the circles passing through the central axes of the rollers 6 and 7 are eccentric with respect to the central axes of the fixed internal gear 3 and the movable internal gear 4. Therefore, the first roller 6 and the second roller 7 are internal gears (fixed internal gear 3 or movable internal gear 4) that face each other at a part of the circumference of each track (the lower side of FIGS. 3 and 4). The tooth groove of the internal gear which is disposed at a position where the tooth groove approaches and engages with the tooth groove (a position where the tooth groove enters the tooth groove) and is opposed to the opposite position (upper side in FIGS. 3 and 4). It is arrange | positioned in the position which is spaced apart and does not engage with.

The number of rollers 6 and 7 is appropriately determined according to the reduction ratio of the corresponding internal gear (fixed internal gear 3 or movable internal gear 4). Specifically, if the reduction ratio of the fixed internal gear 3 is i1 and the reduction ratio of the movable internal gear 4 is i2, the number of teeth of each tooth 3a, 4a is one more than the reduction ratio of the corresponding internal gear. It is set to (i1 + 1), (i2 + 1), or one less number (i1-1), (i2-1). The number of rollers 6 and 7 is set to a divisor of the reduction ratios i1 and i2.

  Then, operation | movement of the reduction gear which concerns on this embodiment is demonstrated.

  When the driving force is input to the input shaft 5 and the input shaft 5 is rotated, the eccentric portion 5a is rotated accordingly, whereby the first roller 6 and the second roller 7 are fixed to the fixed internal gear 3 and the movable internal gear 4. Reciprocating in the radial direction. At this time, the first roller 6 rotates along the tooth groove of the fixed internal gear 3 and moves to the adjacent tooth groove, so that the cage 8 of the fixed internal gear 3 rotates each time the eccentric portion 5a rotates once. Move in the circumferential direction by one tooth. As a result, the cage 8 is decelerated relative to the input shaft 5 and rotates.

  Further, when the cage 8 rotates, the second roller 7 held by the cage 8 also rotates. At the same time, since the second roller 7 also reciprocates in the radial direction accompanying the rotation of the eccentric portion 5a, the second roller 7 moves to the adjacent tooth groove while rotating along the tooth groove of the movable internal gear 4. To do. At this time, when the second roller 7 presses the wall of the tooth gap, the movable internal gear 4 rotates by receiving a circumferential force. Thereby, the movable internal gear 4 rotates by one tooth of the movable internal gear 4 every time the eccentric portion 5 a rotates once, and rotates at a reduced speed with respect to the input shaft 5. Since the movable internal gear 4 rotates with the rotation of the cage 8, the movable internal gear 4 rotates by the number of rotations of the cage 8 in addition to the decelerated rotation accompanying the rotation of the input shaft 5. For this reason, the rotational speed of the movable internal gear 4 is an absolute value of the difference between the rotational speed at the reduced speed accompanying the rotation of the input shaft 5 and the rotational speed of the cage 8.

That is, assuming that the reduction ratio of the fixed internal gear 3 is i1 and the reduction ratio of the movable internal gear 4 is i2, the reduction ratio by the reduction gear according to the present embodiment can be obtained by the following equation (1).

  Reduction ratio = i1 × i2 / | i1-i2 |

For example, the reduction ratio (i1) of the fixed internal gear 3 is 60, and the reduction ratio (i2) of the movable internal gear 4 is 63.
In this case, the reduction ratio is 1260 from Equation 1 above.

  Thus, in the reduction gear according to the present embodiment, high torque can be obtained with a large reduction ratio. In addition, like the speed reducer according to the present embodiment, the fixed internal gear 3 and the movable internal gear 4 are provided, and the rotation is transmitted between the internal gears 3 and 4 and the rollers 6 and 7 to transmit the rotation. By adopting the configuration, it is possible to provide a small reduction gear while maintaining a high output as compared with a countermeasure for increasing the number of teeth of the internal gear in the conventional reduction gear to increase the output.

  Further, in the speed reducer according to the present embodiment, the movable internal gear 4 functions as an output rotator, so that it is easier to ensure rigidity compared to the conventional configuration in which the cage is the output rotator. That is, the movable internal gear 4 has a degree of freedom in the radial direction as compared with the cage and can be formed thick, so that it can sufficiently cope with an increase in torque associated with higher output.

  By the way, when the first roller 6 and the second roller 7 reciprocate in the radial direction along with the rotation of the eccentric portion 5a, the rollers 6, 7 are loaded in various directions from the tooth grooves of the internal gears 3, 4. Receive. And since the load received from a tooth gap acts also on the holder | retainer 8 via each roller 6 and 7, the holder | retainer 8 receives the force which moves to radial direction. As a result, if the cage 8 swings in the radial direction and comes into contact with the teeth of the fixed internal gear 3 or the movable internal gear 4, the rotation of the cage 8 and the movable internal gear 4 is hindered, causing malfunction and transmission of driving force. The efficiency will be reduced. In addition, due to the radial swing of the cage 8, the gap between the cage 8 and the fixed internal gear 3 or the movable internal gear 4 is narrowed, so that the first roller 6 or the second roller 7 is engaged, It may be impossible to rotate.

  Therefore, in the reduction gear according to the present embodiment, the inner peripheral surface of the cage 8 is brought into direct contact with the outer peripheral surface of the rolling bearing (eccentric bearing) 10 in order to prevent the cage 8 from swinging in the radial direction. The inner peripheral surface of the container 8 is guided by the outer peripheral surface of the rolling bearing 10 (see FIG. 1). In the present embodiment, the inner peripheral surface of the cage 8 is in contact with the outer peripheral surface (of the outer ring) of the rolling bearing 10 over the entire circumference (see FIG. 3 or FIG. 4). If the whirling of the direction can be prevented, the inner peripheral surface of the cage 8 comes into contact with the outer peripheral surface of the rolling bearing 10 at a plurality of locations in the circumferential direction (for example, three or four locations arranged at equal intervals in the circumferential direction). You may make it make it. In this way, the inner peripheral surface of the cage 8 is guided by the outer peripheral surface of the rolling bearing 10 to prevent the cage 8 from swinging in the radial direction (moving in the radial direction). It is possible to reliably prevent the cage 8 from interfering with the internal gear 4, and to avoid malfunctions and reductions in driving force transmission efficiency due to these interferences. In addition, by preventing the cage 8 from swinging in the radial direction, the occurrence of biting of the first roller 6 or the second roller 7 can be prevented.

  As described above, according to the speed reducer according to the present embodiment, it is possible to reduce the size and improve the durability while maintaining high output, and further prevent the cage 8 from swinging in the radial direction. Therefore, it is possible to avoid the interference with the internal gears 3 and 4 and the biting of the rollers 6 and 7, so that it is possible to provide a highly reliable reduction gear that is excellent in mountability to vehicles and various devices. For example, the speed reducer according to the present invention can be applied to a variable valve timing device that changes the opening / closing timing of one or both of an intake valve and an exhaust valve of an automobile engine. In addition, the speed reducer according to the present invention is not limited to this, and can be applied to other devices that require a high output with a high reduction ratio.

  5 is a longitudinal sectional view of a reduction gear according to another embodiment of the present invention, FIG. 6 is an exploded perspective view of the reduction gear shown in FIG. 5, and FIG. 7 is a sectional view taken along the line CC in FIG. It is.

  As shown in FIGS. 5 to 7, in the speed reducer 1 according to the present embodiment, in order to prevent the radial swing of the cage 8, the inner circumferential surface of the cage 8 and the outer circumferential surface of the rolling bearing 10 An annular member 14 is disposed between them. The annular member 14 is formed in an annular shape having the same width (same axial dimension) and the same thickness (same radial dimension) over the entire circumference. Other configurations are basically the same as those of the speed reducer according to the embodiment.

  Thus, by arranging the annular member 14 between the inner circumferential surface of the cage 8 and the outer circumferential surface of the rolling bearing 10, the cage 8 can be rotated by the outer circumferential surface of the rolling bearing 10 via the annular member 14. Be guided to. As a result, it is possible to prevent the cage 8 from swinging in the radial direction, and avoid malfunctions and reductions in driving force transmission efficiency due to interference between the cage 8 and the fixed internal gear 3 or the movable internal gear 4. become able to. Further, by preventing the cage 8 from swinging in the radial direction, it is possible to avoid the occurrence of biting of the first roller 6 or the second roller 7. Further, by adopting a configuration in which the annular member 14 is interposed as in the present embodiment, the cage 8 can be formed thinner than the configuration shown in FIGS.

  Further, when the cage 8 rotates, the cage 8 is configured to slide relative to the annular member 14, so that the cage 8 is smoothly rotated. That is, when the annular member 14 functions as a sliding bearing, the cage 8 is smoothly rotated, and the driving force transmission efficiency is improved. Therefore, the annular member 14 is preferably formed of a resin material having slidability.

  In the present embodiment, the annular member 14 is in contact with the inner peripheral surface of the cage 8 and the outer peripheral surface (of the outer ring) of the rolling bearing 10 over the entire circumference (see FIG. 7). 8 can be prevented from swinging in the radial direction, the annular member 14 is arranged at a plurality of locations in the circumferential direction with respect to the inner circumferential surface of the cage 8 and the outer circumferential surface of the rolling bearing 10 (for example, 3 arranged at equal intervals in the circumferential direction). You may make it contact in a place or 4 places.

  In the present embodiment, one annular member 14 is located in the axial center of the cage 8, that is, between the pocket 8a in which the first roller 6 is accommodated and the pocket 8b in which the second roller 7 is accommodated. (See FIG. 5). However, the number and arrangement of the annular members 14 are not limited to this.

  For example, as in the embodiment shown in FIGS. 8 and 9, two annular members 14 may be used, and one annular member 14 may be arranged at each end of the cage 8 in the axial direction. Also in this case, since the cage 8 is rotatably guided by the outer peripheral surface of the rolling bearing 10 via each annular member 14, the cage 8 can be prevented from swinging in the radial direction. In the embodiment shown in FIGS. 8 and 9, the configuration other than the arrangement of the annular member 14 is basically the same as the embodiment shown in FIGS.

  In the embodiment shown in FIGS. 5 to 7 and the embodiment shown in FIGS. 8 and 9, the annular member 14 is configured separately from the cage 8 and the rolling bearing 10, but the annular member 14 is held. The unit 8 or the rolling bearing 10 may be integrated.

  The embodiment of the speed reducer according to the present invention has been described above. However, the present invention is not limited to the above embodiment, and can be implemented in various forms without departing from the gist of the present invention. Of course.

DESCRIPTION OF SYMBOLS 1 Reduction gear 2 Casing 3 Fixed internal gear 3a Teeth 4 Movable internal gear 4a Teeth 5 Input shaft 5a Eccentric part 6 1st roller 7 2nd roller 8 Cage 10 Rolling bearing (bearing member)
14 Ring member

Claims (7)

A casing,
A fixed internal gear fixed to the casing and provided with a plurality of teeth on the inner peripheral surface;
A movable internal gear supported rotatably with respect to the casing and provided with a plurality of teeth on the inner peripheral surface;
An input shaft having an eccentric portion eccentric to the fixed internal gear and the movable internal gear on an outer peripheral surface;
A bearing member disposed on the outer periphery of the eccentric part;
A plurality of first rollers disposed between an inner peripheral surface of the fixed internal gear and the bearing member;
A plurality of second rollers disposed between an inner peripheral surface of the movable internal gear and the bearing member;
A holder for rotatably holding the first roller and the second roller;
Each time the input shaft makes one rotation, the first roller moves in the circumferential direction by one tooth of the fixed internal gear, and the second roller moves in the circumferential direction by one tooth of the movable internal gear. The movable internal gear is a speed reducer that rotates at a reduced speed with respect to the input shaft,
The reduction gear according to claim 1, wherein the bearing member is disposed on an inner periphery of the cage, and is configured to guide the cage rotatably by an outer circumferential surface of the bearing member.   The speed reducer according to claim 1, wherein an inner peripheral surface of the cage is brought into direct contact with an outer peripheral surface of the bearing member.   The annular member is arrange | positioned between the inner peripheral surface of the said holder | retainer, and the outer peripheral surface of the said bearing member, The said retainer was made to contact the outer peripheral surface of the said bearing member via the said annular member. Decelerator.   The speed reducer according to claim 3, wherein the annular member is disposed between a pocket of the cage in which the first roller is accommodated and a pocket of the cage in which the second roller is accommodated.   The speed reducer according to claim 3, wherein the annular member is disposed at both axial ends of the cage.   The speed reducer according to any one of claims 3 to 5, wherein the annular member is a slide bearing.   The speed reducer according to claim 6, wherein the annular member is formed of a resin material having slidability.

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