JP7129308B2 - Eccentric oscillating reduction gear - Google Patents

Description

The present invention relates to an eccentric oscillating speed reducer.

BACKGROUND ART Conventionally, an eccentric oscillating reduction gear transmission including an internal gear and an external gear meshing with the internal gear has been proposed. In this type of speed reducer, the internal teeth of the internal gear may be formed of pin members, and the pin members may be prevented from falling off by a fall-off prevention member (see, for example, Patent Document 1).

JP-A-2006-22829

Under the structure of Patent Document 1, a clearance space is formed between the external gear or the dropout prevention member and the internal gear, and the clearance space is isolated from other spaces. When lubricant is contained in such a gap space, less lubricant is used for lubricating the tooth flanks of each gear, and there is concern about early deterioration of the lubricant.

SUMMARY OF THE INVENTION An aspect of the present invention has been made in view of such circumstances, and one of the purposes thereof is to provide a technique capable of suppressing early deterioration of a lubricant.

One aspect of the present invention relates to an eccentric oscillating reduction gear transmission, comprising: an internal gear integrated with a casing; an external gear meshing with the internal gear; 1 carrier, and a first main bearing arranged between the casing and the first carrier, wherein the internal gear is an internal tooth provided with a pin groove A first drop-out device comprising a gear body and a pin member arranged in the pin groove and forming internal teeth, and arranged between the first main bearing and the external gear to prevent the pin member from falling off. A prevention member is further provided, and between the first main bearing and the first disengagement prevention member, a clearance space between the internal gear body and the first disengagement prevention member and the inside of the first main bearing A radial gap is provided to communicate with the space.

ADVANTAGE OF THE INVENTION According to the aspect with this invention, early deterioration of a lubricant can be suppressed.

1 is a side cross-sectional view of a reduction gear transmission according to a first embodiment; FIG. FIG. 2 is a diagram showing a part of the AA cross section of FIG. 1; FIG. 3 is an enlarged view of FIG. 2; FIG. 2 is an enlarged view of FIG. 1; FIG. 2 is a view showing a part of the BB cross section of FIG. 1; It is a side cross-sectional view of a reduction gear transmission of a second embodiment.

Hereinafter, in the embodiments and modified examples, the same constituent elements are denoted by the same reference numerals, and overlapping descriptions are omitted. In each drawing, for convenience of explanation, some of the constituent elements are omitted as appropriate, or the dimensions of the constituent elements are shown enlarged or reduced as appropriate. As used herein, "contact" includes not only the case where the two parties directly satisfy the mentioned conditions, but also the case where they satisfy the conditions via another member, unless otherwise specified.

(First embodiment)
FIG. 1 is a side cross-sectional view of an eccentric oscillation type reduction gear transmission 10 of the first embodiment. The reduction gear 10 mainly includes an input shaft 12, a crankshaft 14, external gears 16, 18, an internal gear 20, carriers 22, 24, a casing 26, and main bearings 50, 52. Prepare.

The reduction gear 10 can cause one of the external gears 16, 18 and the internal gear 20 to rotate due to the oscillation of the external gears 16, 18, and can output the resulting rotation component from the output member 46 to the driven device. is. Hereinafter, the direction along the central axis CL1 of the internal gear 20 will be referred to as the "axial direction", and the circumferential direction and the radial direction of a circle centered on the central axis CL1 will be referred to as the "circumferential direction" and the "radial direction", respectively. and

The input shaft 12 is rotatable by rotational power input from a driving device (not shown). The drive device is, for example, a motor, gear motor, engine, or the like. The driving device is arranged on one side of the input shaft 12 in the axial direction (the right side in FIG. 1, hereinafter referred to as the input side). Hereinafter, the side opposite to the one side in the axial direction is referred to as the non-input side.

The crankshaft 14 is rotatable around a rotation center line CL2 passing through itself by rotational power input to the input shaft 12 . The input shaft 12 also serves as the crankshaft 14 of this embodiment. The speed reducer 10 of the present embodiment is a center crank type in which the rotation center line CL2 of the crankshaft 14 is coaxial with the center axis line CL1 of the internal gear 20 .

The crankshaft 14 includes a shaft portion 28 extending along the axial direction, and an eccentric body 30 provided rotatably integrally with the shaft portion 28 . The eccentric body 30 has its own axis CL3 eccentric with respect to the rotation center line CL2 of the crankshaft 14, and is capable of causing the external gears 16 and 18 to oscillate. The eccentric body 30 of this embodiment is configured separately from the shaft portion 28 of the crankshaft 14 , but may be configured as a part of the same member as the shaft portion 28 . The crankshaft 14 of this embodiment includes a plurality of eccentric bodies 30, and the phases of the eccentric bodies 30 are out of phase. In this embodiment, two eccentric bodies 30 are provided, and the phases of adjacent eccentric bodies 30 are shifted by 180°.

The external gears 16 and 18 are provided individually corresponding to the plurality of eccentric bodies 30 . The external gears 16 and 18 are rotatably supported by the corresponding eccentric bodies 30 via eccentric bearings 32 . The external gears 16, 18 include a first external gear 16 arranged on the non-input side and a second external gear 18 arranged on the input side.

FIG. 2 is a diagram showing a part of the AA section of FIG. As shown in FIGS. 1 and 2 , the internal gear 20 is provided radially outside the plurality of external gears 16 and 18 and meshes with the external gears 16 and 18 . The internal gear 20 includes a cylindrical internal gear body 34 and internal teeth 36 provided on the inner peripheral portion of the internal gear body 34 . The number of internal teeth (the number of internal teeth 36) of the internal gear 20 is one more than the number of external teeth of the external gears 16, 18 in this embodiment. An internal gear body 34 of the internal gear 20 is integrated with the casing 26 .

3 is an enlarged view of FIG. 2. FIG. As shown in FIGS. 1 and 3, a plurality of pin grooves 38 are provided in the inner peripheral portion of the internal gear body 34 of this embodiment. A plurality of pin grooves 38 are formed at intervals in the circumferential direction. The internal teeth 36 of this embodiment are individually provided corresponding to a plurality of pin grooves 38 , and the first pin members 40 are rotatably supported in the corresponding pin grooves 38 . The first pin member 40 of this embodiment has a cylindrical shape. The pin groove 38 has a cross-sectional shape in which the first pin member 40 can be fitted, more specifically, an arcuate cross-sectional shape.

Return to FIG. The carriers 22 and 24 are a non-input side carrier 22 (first carrier) arranged on the non-input side of the external gears 16 and 18 and an input side carrier 24 (first carrier) arranged on the input side of the external gears 16 and 18 ( second carrier). The carriers 22 , 24 are disk-shaped and rotatably support the input shaft 12 via input shaft bearings 44 .

The casing 26 has a tubular shape as a whole, and the external gears 16 and 18 are arranged inside thereof.

A member that outputs rotational power to the driven device is called an output member 46 , and a member that is fixed to an external member for supporting the reduction gear 10 is called a fixed member 48 . The output member 46 of this embodiment is the counter-input side carrier 22 , and the fixed member 48 is the casing 26 . The output member 46 is rotatably supported by the fixed member 48 via main bearings 50 and 52 .

FIG. 4 is an enlarged view of FIG. Main bearings 50 , 52 include a first main bearing 50 located between casing 26 and non-input carrier 22 and a second main bearing 52 located between casing 26 and input carrier 24 . be

The main bearings 50, 52 are rolling bearings. The main bearings 50, 52 include a plurality of rolling elements 54, an outer ring 56 on which the rolling elements 54 roll, and an inner ring 58 on which the rolling elements 54 roll. A plurality of rolling elements 54 are provided at intervals in the circumferential direction. The rolling elements 54 in this embodiment are spherical bodies, but may be rollers or the like. The plurality of rolling elements 54 are rotatably supported by a retainer (not shown) to retain their relative positions. The outer ring 56 of this embodiment is provided separately from the casing 26 , but the casing 26 may also serve as the outer ring 56 . The inner ring 58 of this embodiment is provided separately from the carriers 22 and 24, but the carriers 22 and 24 may also serve as the inner ring 58.

The speed reducer 10 includes a plurality of second pin members 60 supported by the carriers 22,24. The second pin member 60 is inserted through an insertion hole 62 formed in each of the external gears 16 and 18 . The second pin member 60 is configured by a member separate from each carrier 22, 24, but may be configured by the same member as a part of either carrier 22, 24. The second pin member 60 includes an inner pin 64 that rotates (revolves) integrally with the external gears 16, 18 by receiving the rotation component of the external gears 16, 18 or constrains the rotation thereof. When the anti-input side carrier 22 serves as the output member 46 as in this embodiment, the inner pin 64 revolves, and when the anti-input side carrier 22 serves as the fixed member 48, the inner pin 64 rotates the external gears 16 and 18. constrain the rotation of

The operation of the above reduction gear 10 will be described. When rotational power is transmitted from the driving device to the input shaft 12, the crankshaft 14 rotates around the rotation center line CL2, and the eccentric body 30 causes the external gears 16 and 18 to oscillate. At this time, the external gears 16 and 18 oscillate so that their own shaft cores CL3 rotate around the rotation center line CL2. When the external gears 16, 18 oscillate, the meshing positions of the external gears 16, 18 and the internal gear 20 are sequentially displaced in the circumferential direction. As a result, each time the crankshaft 14 makes one rotation, one of the external gears 16, 18 and the internal gear 20 rotates by the amount corresponding to the difference in the number of teeth between the external gears 16, 18 and the internal gear 20. Occur.

When the opposite input side carrier 22 becomes the output member 46 and the casing 26 becomes the fixed member 48 as in this embodiment, the external gears 16 and 18 rotate. On the other hand, when the casing 26 serves as the output member 46 and the carriers 22 and 24 serve as the fixed members 48, the internal gear 20 rotates. The output member 46 rotates in synchronization with the rotation component of the external gears 16, 18 or the internal gear 20, thereby outputting the rotation component to the driven device. At this time, the rotation of the input shaft 12 is reduced by a reduction ratio according to the difference in the number of teeth between the external gears 16 and 18 and the internal gear 20, and then output to the driven device.

Here, the reduction gear transmission 10 includes drop prevention members 66 , 68 , 70 . The drop-off preventing members 66 , 68 , 70 include the first drop-off preventing member 66 arranged between the external gear 16 and the first main bearing 50 , and the one between the external gear 18 and the second main bearing 52 . A second disengagement prevention member 68 arranged and a third disengagement prevention member 70 arranged between the plurality of external gears 16 and 18 are included.

FIG. 5 is a diagram showing a part of the BB section of FIG. As shown in FIGS. 2, 4, and 5, each drop-off prevention member 66, 68, 70 is ring-shaped. Each drop-off prevention member 66, 68, 70 is arranged at a position where it can contact the plurality of first pin members 40 from the inside in the radial direction, and prevents the first pin member 40 from dropping out of the pin groove 38 by contact with them. do. The first pin member 40 tries to bend and deform by meshing with the external gears 16 and 18 . By using a plurality of fall prevention members 66 , 68 , 70 , such bending deformation of the first pin member 40 can be effectively suppressed.

The first drop-off prevention member 66 is arranged between one end of the first pin member 40 on the counter-input side (one side in the axial direction) and the counter-input side carrier 22 (first carrier). The second drop-off prevention member 68 is arranged between the other end of the first pin member 40 on the input side (the other side in the axial direction) and the input-side carrier 24 (second carrier). The third fall prevention member 70 is arranged between the first pin member 40 and the second pin member 60 .

The third disengagement prevention member 70 also has the role of restricting axial movement of the plurality of external gears 16 and 18 by coming into contact with them. In this embodiment, the external gears 16 and 18 are also in contact with other members (carriers 22 and 24) arranged on the opposite side in the axial direction from the third disengagement prevention member 70, thereby restricting their axial movement. be done. It should be noted that the third drop-off preventing member 70 does not have to have the function of preventing the first pin member 40 from dropping off.

Outer diameters R1, R2, R3 of the drop-off prevention members 66, 68, 70 are set to be substantially the same. The term "substantially" as used in this specification is not limited to the case where the mentioned conditions are strictly satisfied, but also includes the case where the position is shifted by an error such as a dimensional tolerance or a manufacturing error. The outer diameters R1, R2, R3 of the anti-dropping members 66, 68, 70 can form a slight clearance (not shown) between the pin groove 38 or between the anti-dropping members 66, 68, 70 and the first pin member 40. set to size. This clearance is provided to allow rotation of the plurality of first pin members 40 .

The first drop-off prevention member 66 is provided with a slight gap 72 between it and the carrier 22 on the counter-input side. The second drop-off prevention member 68 is provided with a slight gap 74 between itself and the input side carrier 24 . Thereby, when the carriers 22 and 24 rotate on their own axes, it is possible to avoid the occurrence of sliding resistance between them and the fall prevention members 66 and 68 . The radial dimensions of the gaps 72 and 74 are larger than the radial clearance between the pin groove 38 or the drop-off prevention members 66 , 68 and 70 and the first pin member 40 .

The internal gear main body 34 forms a clearance space 78 in which a lubricant 76 is contained between other members. Lubricant 76 is, for example, grease, lubricating oil, or the like. Here, "another member" refers to a member facing radially inwardly of the internal gear body 34, and in the present embodiment, the drop-off prevention members 66, 68, 70 and the external gears 16, 18 correspond. .

The gap space 78 of the present embodiment consists of a first space 80 formed between the internal gear body 34 and the external gears 16 and 18 and between the internal gear body 34 and the drop-off prevention members 66, 68 and 70. A second space 82 is formed. The first space 80 and the second space 82 communicate with each other. The radial dimension of the first space 80 changes as the external gears 16 and 18 oscillate. As the radial dimension of the first space 80 changes, the lubricant 76 in the first space 80 can flow throughout the entire circumferential direction. The second space 82 is configured by a plurality of inter-pin spaces 84 (see FIG. 3) formed between adjacent first pin members 40 .

The clearance space 78 of the present embodiment is radially separated from an inner space 86 formed radially inside the clearance space 78 in an axial range Ra radially overlapping the first pin member 40 . The inner space 86 is radially separated from the clearance space 78 by the external gears 16 and 18 and the anti-falling members 66, 68 and 70, which are the "other members" described above. These external gears 16 , 18 and the drop-off prevention members 66 , 68 , 70 function as isolation members that radially isolate the clearance space 78 from the inner space 86 . This inner space 86 is formed between the separating members or carriers 22 , 24 and the crankshaft 14 .

"Isolation" here means isolation to completely block the flow of lubricant 76 between the two objects referred to (clearance space 78 and inner space 86), as well as Isolation to allow slight flow of agent 76 is included. This slight flow of lubricant 76 occurs, for example, between a plurality of isolation members or between the isolation members and other members (main bearings 50, 52, carriers 22, 24, etc.).

Between the first main bearing 50 and the first disengagement prevention member 66, there is provided a first radial direction connecting the inner space 94 of the first main bearing 50 (hereinafter referred to as the first bearing inner space 94) and the clearance space 78. A gap 88 is provided. The first bearing internal space 94 is the space between the outer ring 56 and the inner ring 58 of the first main bearing 50 . The clearance space 78 here refers to the clearance space between the internal gear body 34 and the first drop-off prevention member 66 . A radial gap here refers to a gap that extends radially between the two objects being referred to.

A first radial gap 88 is formed between the outer ring 56 of the first main bearing 50 and the first disengagement prevention member 66 at the locations (surfaces) where the first main bearing 50 and the first disengagement prevention member 66 face each other in the axial direction. provided in Specifically, the first radial gap 88 is defined by a first inner peripheral edge portion 90 on the side of the first drop-off prevention member 66 in the axial direction of the inner peripheral portion of the outer ring 56 and an outer peripheral portion of the first drop-off prevention member 66 . and the first outer peripheral edge portion 92 on the side where the first main bearing 50 is located in the axial direction. In this embodiment, no radial clearance is provided between the inner ring 58 of the first main bearing 50 and the first drop-out prevention member 66 . That is, the inner ring 58 of the first main bearing 50 and the first disengagement prevention member 66 are in axial contact over the entire circumference.

Between the second main bearing 52 and the second disengagement prevention member 68, a second radial direction connecting the inner space 102 of the second main bearing 52 (hereinafter referred to as the second bearing inner space 102) and the clearance space 78 is provided. A gap 96 is provided. The second bearing internal space 102 is the space between the outer ring 56 and the inner ring 58 of the second main bearing 52 . The clearance space 78 here refers to the clearance space between the internal gear main body 34 and the second disengagement prevention member 68 .

A second radial gap 96 is formed between the outer ring 56 of the second main bearing 52 and the second disengagement prevention member 68 at the locations (surfaces) where the second main bearing 52 and the second disengagement prevention member 68 face each other in the axial direction. provided in More specifically, the second radial clearance 96 is formed by a second inner peripheral edge portion 98 on the side of the second drop-off prevention member 68 in the axial direction of the inner peripheral portion of the outer ring 56 and an outer peripheral portion of the second drop-off prevention member 68 . and the second outer peripheral edge portion 100 on the side where the second main bearing 52 is located in the axial direction. In this embodiment, no radial clearance is provided between the inner ring 58 of the second main bearing 52 and the second drop-out prevention member 68 . That is, the inner ring 58 of the second main bearing 52 and the second disengagement prevention member 68 are in axial contact over the entire circumference.

The casing 26 forms an outer peripheral space 104 including a clearance space 78 between itself and other members. The outer peripheral space 104 of this embodiment includes the first bearing inner space 94 and the second bearing inner space 102 in addition to the gap space 78 described above. Further, in the outer peripheral space 104 of the present embodiment, a third bearing is formed between the casing 26 and the counter-input side carrier 22 on the opposite side of the gap space 78 in the axial direction with respect to the first bearing internal space 94 . A space 106 is included. The “other member” here refers to a member that faces the casing 26 radially inward. In this embodiment, the drop-off prevention members 66, 68, 70, the external gears 16, 18, and the carriers 22, 24 correspond.

The outer space 104 is sealed by a first sealing member 108 arranged on the opposite input side (one side in the axial direction) of the first pin member 40 . The first sealing member 108 of this embodiment is an oil seal arranged between the casing 26 and the non-input side carrier 22 .

The outer space 104 is sealed by a second sealing member 110 arranged on the input side (the other side in the axial direction) with respect to the first pin member 40 . The second sealing member 110 of this embodiment is a bearing seal incorporated in the second main bearing 52 . The second sealing member 110 is arranged closer to the input side than the rolling elements 54 of the second main bearing 52 . The second sealing member 110 is also understood to be arranged between the casing 26 and the input side carrier 24 .

The outer space 104 of the present embodiment is isolated from the inner space 86 even outside the axial range Ra radially overlapping the first pin member 40 . Lubricant (not shown) for lubricating moving parts such as the external gears 16 and 18 and the eccentric bearing 32 is also enclosed in the inner space 86 as described above.

The effect of the above reduction gear 10 will be described.

(A) A first radial clearance 88 is provided between the first main bearing 50 and the first drop-off prevention member 66 . Therefore, the lubricant 76 can be exchanged between the first bearing internal space 94 of the first main bearing 50 and the clearance space 78 through the first radial clearance 88 . This is accomplished by the movement of the rolling elements 54 of the first main bearing 50 and the external gears 16 , 18 causing the lubricant 76 in the clearance space 78 and the first bearing internal space 94 to flow. Accordingly, the amount of the lubricant 76 used for lubricating the tooth flanks of the gears 16, 18, 20 can be increased, and early deterioration of the lubricant 76 in the gap space 78 can be suppressed.

(B) A second radial gap 96 is provided between the second main bearing 52 and the second drop-off prevention member 68 . Therefore, the lubricant 76 can also be exchanged between the second bearing inner space 102 of the second main bearing 52 and the clearance space 78 through the second radial clearance 96 . This is achieved by the movement of the rolling elements 54 of the second main bearing 52 and the external gears 16 , 18 causing the lubricant 76 in the clearance space 78 and the inner space 102 of the second bearing to flow. Accordingly, the amount of the lubricant 76 used for lubricating the tooth flanks of the gears 16, 18, 20 can be further increased, and early deterioration of the lubricant 76 in the gap space 78 can be further suppressed.

(C) The speed reducer 10 is provided with a third fall prevention member 70 which is arranged between the two external gears 16 and 18 and which prevents the first pin member 40 from falling off. As a result, the second space 82, which is part of the clearance space 78, can be formed between the internal gear body 34 and the third disengagement prevention member 70, and the volume of the clearance space 78 can be increased accordingly. Accordingly, the amount of the lubricant 76 used for lubricating the tooth flanks of the gears 16, 18, 20 can be further increased, and early deterioration of the lubricant 76 in the gap space 78 can be further suppressed.

(D) No radial clearance is provided between the inner ring 58 of the first main bearing 50 and the first drop-out prevention member 66 . Therefore, it becomes difficult for the lubricant 76 to leak from the first bearing inner space 94 to the inner space 86 through these spaces, and the lubricant 76 is easily retained in the clearance space 78 .

(E) No radial clearance is provided between the inner ring 58 of the second main bearing 52 and the second drop-off prevention member 68 . Therefore, it is difficult for the lubricant 76 to leak from the second bearing inner space 102 to the inner space 86 through these spaces, and the lubricant 76 can be easily retained in the clearance space 78 .

(F) The clearance space 78 in which the lubricant 76 is enclosed is radially separated from the inner space 86 radially inward in the axial range Ra radially overlapping the first pin member 40 . Therefore, it becomes difficult for the lubricant 76 to spread from the clearance space 78 to the inner space 86 , and the lubricant 76 is easily retained in the clearance space 78 .

The outer space 104, including the interstitial space 78, is sealed by respective sealing members 108,110 disposed between the casing 26 and the carriers 22,24. Therefore, the lubricant 76 is less likely to leak from the outer peripheral space 104 to other spaces, and the lubricant 76 can be more easily retained in the clearance space 78 .

By retaining the lubricant 76 in the clearance space 78 in this way, it is possible to stably suppress the oil film shortage of the lubricant 76 on the tooth flanks of the gears 16 , 18 , and 20 forming the clearance space 78 . Along with this, the life of each gear 16, 18, 20 can be extended. In particular, when using the lubricant 76 with low fluidity, this advantage can be greatly obtained.

Other features of the reduction gear transmission 10 of this embodiment will be described. Please refer to FIGS. The internal gear body 34 is provided with an annular groove 114 . When the external gears 16 and 18 oscillate, the external teeth 112 of the external gears 16 and 18 enter the annular groove 114, thereby avoiding interference with the internal gear body 34. The annular groove 114 is provided individually corresponding to each of the external gears 16 and 18 and formed radially outwardly of the corresponding external gears 16 and 18 . The annular groove 114 has a larger axial dimension than the corresponding external gears 16,18.

The internal gear body 34 includes an annular protrusion 116 that forms an annular groove 114 and protrudes radially inward. The plurality of pin grooves 38 described above are formed in the inner peripheral portion of the annular protrusion 116, and the fall prevention members 66, 68, 70 described above are arranged radially inside.

(G) The annular groove 114 forms the gap space 78 described above and constitutes a lubricant reservoir for storing the lubricant 76 . Thereby, the volume of the gap space 78 can be increased. Accordingly, the amount of the lubricant 76 used for lubricating the tooth flanks of the gears 16, 18, 20 can be further increased, and early deterioration of the lubricant 76 in the gap space 78 can be further suppressed.

(Second embodiment)
FIG. 6 is a side sectional view of the reduction gear transmission 10 of the second embodiment. The outer space 104 including the clearance space 78 of this embodiment communicates with other spaces. explain in detail.

The casing 26 is provided on the input side with respect to the input side carrier 24 and has a through wall portion 26b formed with a through hole 26a through which the input shaft 12 passes. A fourth space 118 is formed between the through wall portion 26 b of the casing 26 and the input side carrier 24 .

The speed reducer 10 does not include the second sealing member 110 described above, and the outer space 104 communicates with the fourth space 118 . The fourth space 118 is sealed by a third sealing member 120 such as an oil seal arranged between the through hole 26a of the casing 26 and the input shaft 12, for example. In this embodiment as well, the effects (A) to (G) described above can be obtained.

Even if the lubricant 76 leaks from the outer peripheral space 104 to another space (fourth space 118 ), the flow of the lubricant 76 can return the lubricant 76 to the original gap space 78 . In particular, when the lubricant 76 with high fluidity is used, it becomes easy to return the lubricant 76 in this manner. Therefore, in the present embodiment as well, it is possible to easily retain the lubricant 76 in the clearance space 78 as described in (D) to (F) above, as in the first embodiment.

The present invention has been described above based on the embodiments. Next, modified examples of each component will be described.

Although the eccentric oscillating speed reducer of the embodiment has been described as an example of the center crank type, the type is not particularly limited. For example, it may be applied to a distribution type eccentric oscillating reduction gear transmission in which a plurality of crankshafts 14 are arranged at positions offset from the center axis CL1 of the internal gear 20 .

The output member 46 may be the casing 26 and the fixed member 48 may be the carriers 22,24.

The reduction gear 10 may have at least two external gears 16, 18 as in this embodiment. This means that one or more external gears different from the external gears 16, 18 may be provided. The reduction gear 10 may have only one external gear 16,18. When three or more external gears 16 , 18 are provided, the third drop-out prevention member 70 may be arranged between all the external gears 16 , 18 . In addition, the third drop-off prevention member 70 may not be arranged between all or part of the external gears 16 and 18.

An example has been described in which the first carrier is the anti-input carrier 22 and the second carrier is the input carrier 24 . The first carrier may be the input side carrier 24 and the second carrier may be the counter-input side carrier 22 . In either case, the reduction gear transmission 10 may have only the first carrier and not have the second carrier. In this case, the speed reducer 10 does not need to include the second main bearing 52 and the second drop-off prevention member 68 in addition to the second carrier.

The annular groove 114 may not be formed in the internal gear body 34 .

The gap space 78 and the inner space 86 are formed by the aforementioned separating members (external gears 16, 18, drop-off prevention members 66, 68, 70) in the axial range Ra overlapping the first pin member 40 in the radial direction. may be communicated via a space of

Although the example in which the first sealing member 108 is an oil seal has been described, the specific example is not particularly limited. The first sealing member 108 may be, for example, a bearing seal incorporated into the first main bearing 50 . Although the example in which the second sealing member 110 is a bearing seal has been described, the specific example is not particularly limited. Second sealing member 110 may be, for example, an oil seal.

The first radial gap 88 may also be provided between the inner ring 58 of the first main bearing 50 and the first drop-off prevention member 66 . The second radial gap 96 may also be provided between the inner ring 58 of the second main bearing 52 and the second drop-off prevention member 68 .

The embodiments and modifications of the present invention have been described in detail above. All of the above-described embodiments and modifications merely show specific examples for carrying out the present invention. The contents of the embodiments and modifications do not limit the technical scope of the present invention, and many design changes such as alterations, additions, and deletions of constituent elements are possible without departing from the spirit of the invention. In the above-described embodiment, the content that allows such design changes is emphasized by adding notations such as "of the embodiment" and "in the embodiment", but even contents without such notation can be designed. Changes are allowed. Any combination of the above components is also effective as an aspect of the present invention. The hatching attached to the cross section of the drawing does not limit the material of the hatched object.

DESCRIPTION OF SYMBOLS 10... Eccentric oscillating type reduction gear, 16... 18... External gear, 20... Internal gear, 22... Anti-input side carrier (first carrier), 24... Input side carrier (second carrier), 26... Casing, 34... Internal gear body, 36... Internal tooth, 38... Pin groove, 40... First pin member, 50... First main bearing, 52... Second main bearing, 56... Outer ring, 58... Inner ring, 66... First Anti-dropping member 68 Second anti-dropping member 70 Third anti-dropping member 76 Lubricant 78 Gap space 86 Inner space 88 First radial gap 96 Second radial gap , 114...an annular groove.

Claims (5)

an internal gear integrated with the casing;
an external gear meshing with the internal gear;
a first carrier disposed on one axial side of the external gear;
An eccentric oscillating type reduction gear transmission comprising a first main bearing arranged between the casing and the first carrier,
The internal gear has an internal gear body provided with a pin groove, and a pin member arranged in the pin groove and forming an internal tooth,
further comprising a first fall-off prevention member disposed between the first main bearing and the external gear to prevent the pin member from falling off;
Between the first main bearing and the first disengagement prevention member, there is provided a diameter that communicates a clearance space between the internal gear body and the first disengagement prevention member and an internal space of the first main bearing. A directional gap is provided ,
The first disengagement prevention member is a separate member from the outer ring and the inner ring of the first main bearing, and is arranged to face the inner ring of the first main bearing in the axial direction. The eccentric oscillating type speed reducer that provides the radial clearance between the The first drop-off prevention member is arranged radially between the first carrier and the pin member,
A radial gap is provided between the first drop-off prevention member and the first carrier,
2. The method according to claim 1, wherein a radial clearance between said first drop-off preventing member and said first carrier is larger than a radial clearance between said pin groove or between said first drop-off preventing member and said pin member . The eccentric oscillating type speed reducer as described. 3. The eccentric rocker according to claim 1, wherein a first outer peripheral edge portion of the outer peripheral portion of the first coming-off prevention member, which is located on the side of the first main bearing, is located radially outward of an inner ring of the first main bearing. Dynamic reduction gear. A first inner peripheral edge portion of the inner peripheral portion of the outer ring of the first main bearing located on the first disengagement prevention member side is positioned radially inward of the inner peripheral surface of the internal gear body,
The radial gap is provided between the first outer peripheral edge portion on the first main bearing side and the first inner peripheral edge portion of the outer ring of the first main bearing on the outer peripheral portion of the first disengagement prevention member. 4. The eccentric oscillating type speed reducer according to any one of claims 1 to 3. The internal gear body has an annular groove for avoiding interference with the external gear,
The eccentric oscillating type reduction gear transmission according to any one of claims 1 to 4, wherein the annular groove constitutes a lubricant reservoir for storing lubricant.

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