JP5654798B2 - Roller retainer and swinging intermeshing gear device - Google Patents

Description

  The present invention relates to a retainer for a roller and a swinging intermeshing gear device incorporating the retainer.

  Japanese Patent Application Laid-Open No. 2004-133867 discloses a swinging intermeshing gear device. In this gear device, the external gear meshes with the internal gear while swinging. A plurality of rollers are arranged between the external gear and the eccentric body that swings the external gear. The plurality of rollers are held by a retainer. The retainer includes a pair of ring bodies that define positions of both ends of each of the plurality of rollers, and a coupling body that couples the pair of ring bodies and defines circumferential positions of the plurality of rollers. .

  This oscillating internal meshing gear device includes a plurality of external gears, and a plurality of rollers (and retainers thereof) are incorporated in each external gear. Adjacent ring bodies of each retainer are in contact with each other. In this Patent Document 1, for the two adjacent retainers, a virtual torus defined by the first retainer coupling body and a virtual torus defined by the second retainer coupling body are assumed. In addition, the size of the connecting body of the two retainers is set so that the two virtual toric bodies overlap each other in the entire circumferential direction when viewed from the axial direction.

  In Patent Document 1, with such a configuration, even when a torque is applied to the gear device and the roller held by one retainer tries to tilt, the torque is received by the connecting body of the adjacent retainer, The roller is prevented from tilting.

Japanese Patent Laying-Open No. 2010-32000 (FIG. 3)

  In the oscillating internal meshing gear device having a plurality of external gears, as in the gear device disclosed in Patent Document 1, the axial direction of the rollers arranged between the eccentric bodies and the external gears In general, the positioning is performed by contact between the ring bodies of the retainer.

  However, each roller and its retainer (because it is arranged on the outer periphery of the eccentric body) each time the shaft on which the eccentric body is provided makes one rotation, the distance from the shaft center of the shaft corresponds to the amount of eccentricity. It will change as much as you do. Therefore, in order to keep the ring bodies of the adjacent retainers always in contact with each other, the radial dimension (width) of the ring bodies must be correspondingly large. As a result, there is a problem that the lubricant is difficult to enter from the gap between the ring bodies and the roller is not smoothly lubricated.

  In particular, in the case of a retainer configured to prevent the ring body from being inclined due to the reinforcing effect of the connecting body as in the gear device disclosed in Patent Document 1, the contact surface between adjacent ring bodies is always perfect. Since the pressed state is maintained, the lubricant is less likely to enter the roller side, which may further reduce the lubricity.

  The present invention has been made to solve such a conventional problem, and is a retainer capable of further improving the lubricity of the roller while stably holding the roller, and the retainer incorporated therein. An object of the present invention is to provide a swinging intermeshing gear device having high lubrication performance.

The present invention is a retainer for holding a plurality of rollers, and a pair of ring bodies for positioning the positions of both ends of the plurality of rollers, and the circumference of the plurality of rollers. comprising a connecting member for positioning the direction position, a, and the inner diameter of the coupling body, the is set smaller than a pair of ring members both inside diameter, radial length of the connecting member is, the pair The above-described problem is solved by adopting a configuration that is larger than the radial length of both ring bodies .

  In the retainer having the same basic configuration, at least a part of the outer diameter of the coupling body is set larger than the outer diameter of at least one of the pair of ring bodies. By adopting a configuration, the above-described problem is solved.

In the retainer according to the present invention, the inner diameter of the "coupling body is set to be smaller than the inner diameter of both the pair of ring members, the radial length of the connecting member is greater than the radial length of both the pair of ring members when "the coupling body for projecting relatively radially inward from the ring body, the inner peripheral end of the roller is relaxed situation which is closed by the ring body.

On the other hand, in the retainer according to the present invention, “the outer diameter of the coupling body is set larger than the outer diameters of both the pair of ring bodies, and the radial length of the coupling body is the radial direction of both of the pair of ring bodies. when greater length ", connected body for projecting relatively radially outward from the ring member, the outer peripheral side of the end portion of the roller is relaxed situation which is closed by the ring body.

  In either case of the retainer, since the situation where the end of the roller is blocked by the ring body is alleviated, the lubricant can easily enter the roller side beyond the ring body from the outside in the axial direction of the retainer. In addition, since the connecting body itself has a portion protruding from the ring body, the length in the radial direction can be ensured to be long, so that each roller can be stably held.

  The roller retainer according to the present invention can exert its original function particularly when applied to holding a roller disposed between the eccentric body and the external gear of the swinging intermeshing gear device. .

  According to the present invention, it is possible to obtain a retainer capable of further enhancing the lubricity of the roller while stably holding the roller, and a swinging intermeshing gear device incorporating the retainer and having high lubrication performance. Can do.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an overall schematic diagram of a swinging intermeshing gear device incorporating a retainer according to an example of an embodiment of the present invention. Fig. 1 is an enlarged view of the main part near the retainer in Fig. 1. The perspective view which shows a mode that this retainer hold | maintains a roller (A) Top view, (B) Front view of a partially broken view, and (C) Side view showing a state in which the retainer similarly holds the roller. 4 is an enlarged cross-sectional view of the portion indicated by the arrow V in the front view of FIG. 4 is an enlarged cross-sectional view of the portion indicated by arrow VI in the side view of FIG. Sectional drawing of the retainer which concerns on an example of other embodiment of this invention. 7 is an enlarged cross-sectional view of the portion indicated by arrow VIII in FIG. (A) Partially broken sectional view and (B) plan view of a retainer showing an example of still another embodiment of the present invention 9 is an enlarged cross-sectional view of the portion indicated by an arrow X in FIG. Enlarged cross-sectional view of the arrow XI portion of FIG.

  Hereinafter, an example of an embodiment of the present invention will be described in detail based on the drawings.

  FIG. 1 is an overall schematic view of a swinging intermeshing gear device incorporating a retainer according to an example of an embodiment of the present invention. First, the schematic configuration of the swinging intermeshing gear device will be briefly described together with the operation.

  The oscillating internal meshing gear device 12 includes a plurality of (in this example, two) external gears 18 and 20 that are oscillated and rotated by eccentric bodies 14 and 16, and the external gears 18 and 20 are internally connected. And an internal gear 22 that meshes. The eccentric bodies 14 and 16 are integrally formed on the input shaft 24.

  A plurality of rollers 26, 28 are arranged on the outer circumferences of the eccentric bodies 14, 16, and the external gears 18, 20 are incorporated outside the plurality of rollers 26, 28. The retainers 30 and 32 according to the embodiment of the present invention hold a plurality of rollers 26 and 28 disposed between the eccentric bodies 14 and 16 and the external gears 18 and 20 (described later).

  The external gears 18 and 20 have slightly fewer teeth than the internal gear 22. For this reason, when the external gears 18 and 20 are inwardly meshed with the internal gear 22 while swinging, a slow relative rotation occurs between the external gears 18 and 20 and the internal gear 22. Here, inner pin holes 18A and 20A are formed in the external gears 18 and 20, and an inner pin 36 fixed to the casing 34 passes through the inner pin holes 18A and 20A. That is, the rotation component of the external gears 18 and 20 and the rotation component of the casing 34 are synchronized. The internal gear 22 is rotatably supported by the casing 34 via a cross roller 38 and is integrated with a flange body 42 via a bolt 40.

  From the above configuration, the swinging intermeshing type gear device 12 is constrained to rotate by the inner pin 36 integrated with the casing 34 when the casing 34 is fixed to an external member (not shown). ) The relative rotation of the internal gear 22 with respect to the external gears 18 and 20 is output via the flange body 42. Further, when the flange body 42 (and the internal gear 22) is fixed, the relative rotation of the external gears 18 and 20 with respect to the internal gear 22 is output via the internal pin 36 and the casing 34 (so-called frame rotation). output).

  The internal space of the gear unit 12 is sealed by oil seals 44, 46, and 48, and grease (lubricant) is enclosed. Reference numeral 50 in FIG. 1 denotes a grease supply hole. The grease sealed from the greasing hole 50 is guided to the axial side portions of the two retainers 30 and 32 through the introduction path 52 formed in the radial direction.

  Hereinafter, the structure near the retainers 30 and 32 will be described in detail.

  FIG. 2 is an enlarged view of a main part in the vicinity of the retainers 30 and 32 of FIG. As is clear from the depictions of FIGS. 1 and 2, in this embodiment, the two retainers 30 and 32 have the same shape, and the eccentric bodies 14 and 16 and the external gear 18 and the like. 20 are incorporated symmetrically with each other (back to back). Therefore, in the following description, it explains together suitably.

  3 is a perspective view showing a state in which the retainer 30 holds the roller 26, FIG. 4 shows a state in which the retainer 30 similarly holds the roller 26, and (A) is a plan view. (B) is a partially broken front view, and (C) is a side view.

  The retainer 30 (32) is formed of a resin containing glass fiber, and a pair of first and second ring bodies 30A and 30B (32A and 32B) that define both axial positions of the plurality of rollers 26 (28). And a coupling body 30C (32C) that couples the pair of first and second ring bodies 30A, 30B (32A, 32B). The glass fiber content is 35% in this embodiment. In the structure where the retainers 30 (32) rub against each other as in the present embodiment, in order to prevent wear of the second ring body 30B (32B) of the retainer 30 (32), the glass fiber content is preferably 10-40% is preferable and 25-40% is especially preferable.

  The coupling body 30C (32C) defines the circumferential position of each roller 26 (28) by being positioned between the circumferential directions of the rollers 26 (28).

  In this embodiment, the inner diameter D1 (D2) of the coupling body 30C (32C) of the retainer 30 (32) is equal to the inner diameters D3, D4 (D5, D2) of the first and second ring bodies 30A, 30B (32A, 32B). It is set smaller than D6). That is, the connecting body 30C (32C) protrudes radially inward by Δ1 from the first and second ring bodies 30A, 30B (32A, 32B). In other words, when the first and second ring bodies 30A, 30B (32A, 32B) are viewed from the axial direction, the inside of the end portion 26A (28A) of the coupling body 30C (32C) and the roller 26 (28). A situation is formed in which the peripheral side appears to be exposed. In this embodiment, the inner diameters D3 and D5 of the first ring bodies 30A and 32A and the inner diameters D4 and D6 of the second ring bodies 30B and 32B are all the same.

  In this embodiment, the connecting body 30C (32C) has an inner diameter D1 (D2) smaller than the inner diameters D3 and D4 (D5 and D6) of the first and second ring bodies 30A and 30B (32A and 32B). The axial length L1 (L2) of the portion (hereinafter referred to as a protruding portion) P1 (P2) is shorter than the axial length L3 (L4) of the roller 26 (28). As a result, a gap δ1 (δ2) is secured between the ring plate 51 and the protrusion 48 for positioning the roller 26 (28) in the axial direction and the protruding portion P1 (P2). That is, in the connecting body 30C (32C), the projecting portion P1 (P2) is formed over the entire distance L5, L6 (L7, L8) between the first and second ring bodies 30A, 30B (32A, 32B). It has not been done.

  In the present embodiment, the retainer 30 (32) is positioned within the gear unit 12 by sandwiching the roller 26 (28) together with the retainer 30 (32) between the ring plate 51 and the protrusion 48. . The gap δ1 (δ2) contributes to prevention of interference between the ring plate 51 and the protrusion 48 and the protruding portion P1 (P2) of the coupling body 30C (32C). On the second ring body 30B (32B) side, the clearance for the gap δ1 (δ2) is not particularly formed. This is because the side of the second ring body 30B (32B) is a side to be slid with each other, so that the problem of interference with the ring plate 51 and the protrusion 48 does not occur. It is. In other words, the protruding portion P1 (P2) is displaced from the center of the roller 26 (28) toward the axial anti-projection portion side (anti-ring plate side).

  In this embodiment, the outer diameters d1 and d2 (d3 and d4) of the first and second ring bodies 30A and 30B (32A and 32B) are the same as the outer diameter d5 (d6) of the coupling body 30C (32C). It is said that. In this embodiment, the lengths L11 and L12 in the radial direction of the first ring bodies 30A and 32A and the lengths L13 and L14 in the radial direction of the second ring bodies 30B and 32B are also the same.

  As is apparent from FIGS. 3 to 6, in this embodiment, a claw for preventing the roller 26 (28) from dropping inward in the radial direction at the radially inner end of the coupling body 30 C (32 C). A portion 30C1 (32C1: not shown) is formed. The claw portion 30C1 (32C1) may be formed over the entire axial length of the coupling body 30C (32C), but in this embodiment, both axial end portions of the protruding portion P1 (P2) of the coupling body 30C (32C). It is formed only on. That is, the claw portion is not formed at the axially central portion of the coupling body 30C (32C).

  In this embodiment, a single V-shaped recess 60 (62) serving as a grease passage is formed along the circumferential direction at the axially central portion on the outer peripheral side of the coupling body 30C (32C). . The shape of the recess is not necessarily V-shaped, and may be U-shaped or semi-circular, for example. In this example, only one recess 60 (62) is formed, but two or more recesses 60 (62) may be formed. The forming position is also the central portion in the axial direction in this example, but it is not necessarily the central portion and may be closer to either side. Furthermore, in this example, the recess 60 (62) is formed on the outer peripheral side of the coupling body 30C (32C), but it may be formed on the inner peripheral side (or also on the inner peripheral side) ( For example, see the examples of FIGS. 9 and 10 described later).

  In this embodiment, the length L7 (L8) in the radial direction of the base end portion 30C2 (32C2) of the coupling body 30C (32C) adjacent to the first and second ring bodies 30A and 30B (32A and 32B) is as follows. The recess 60 (62) is set to be larger than the radial length L9 (L10). This is because the base end portion 30C2 (32C2) of the connecting body 30C (32C) inevitably tends to concentrate stress due to its shape, and therefore the recess 60 (62) that promotes stress concentration is provided on the base end portion 30C2 (32C2). This is because it is not preferable to form the end 30C2 (32C2). Based on this point, in this embodiment, no recess is formed in the base end portion 30C2 (32C2) of the coupling body 30C (32C) adjacent to the first and second ring bodies 30A, 30B (32A, 32B). .

  Next, the operation of the retainer 30 (32) according to this embodiment will be described.

  According to the oscillating intermeshing gear device 12 according to the present embodiment, the plurality of rollers 26 and 28 are disposed between the eccentric bodies 14 and 16 and the external gears 18 and 20, and the eccentric bodies 14 and 16. The sliding resistance when the external gears 18 and 20 oscillate on the outer periphery is reduced.

  The plurality of rollers 26 (28) have their axial positions defined by the first and second ring bodies 30A, 30B (32A, 32B) of the retainer 30 (32), and are circumferentially defined by the connecting body 30C (32C). The position of is defined.

  Here, in the retainer 30 (32) according to this embodiment, the inner diameter D1 (D2) of the coupling body 30C (32C) is the inner diameter D3, D4 of the first and second ring bodies 30A, 30B (32A, 32B). It is set smaller than (D5, D6), and the connecting body 30C (32C) protrudes radially inward by Δ1 from the first and second ring bodies 30A, 30B (32A, 32B). Therefore, the situation where the inner peripheral side of the end portion 26A (28A) of the roller 26 (28) is closed by the first and second ring bodies 30A, 30B (32A, 32B) is alleviated, and the retainer 30 (32) is axially moved. From the perspective, the coupling body 30C (32C) and a part of the end portion 26A (28A) of the roller 26 (28) are exposed radially inward of the first and second ring bodies 30A, 30B (32A, 32B). A visible situation is formed.

  With this configuration, the grease sealed from the greasing hole 50 is easily blocked by the first ring body 32A of the retainer 32 and easily passes the inner side in the radial direction of the first ring body 32A in the axial direction. Can enter. Further, it can easily enter the retainer 30 on the roller 26 side through the second ring body 32B of the retainer 32 and the second ring body 30B of the retainer 30. At this time, a recess 60 (62) serving as a grease passage is formed along the circumferential direction at the axially central portion on the outer peripheral side of the coupling body 30C (32C), and the roller 26 (28) is prevented from coming off. Since the claw portion 30C1 (32C1) formed for the purpose is also formed only at both axial end portions of the projecting portion P1 (P2) of the coupling body 30C (32C), the grease is the recess 60 (62) It is possible to satisfactorily reach the entire periphery of each roller 26 (28) through a portion where the claw portion 30C1 (32C1) is not formed.

  On the other hand, in this embodiment, this nail | claw part 30C1 (32C1) is formed in the "both ends" of the axial direction of the protrusion part P1 (P2) of the connection body 30C (32C). Further, the connecting body 30C (32C) itself protrudes radially inward from the first and second ring bodies 30A, 30B (32A, 32B), and a large radial length L7 (L8) can be secured. For this reason, the plurality of rollers 26 (28) can be held in an extremely stable state without being inclined (without being skewed).

  Furthermore, even if the roller 26 (28) is removed from the outer periphery of the eccentric bodies 14 and 16 together with the retainer 30 (32), the plurality of rollers 26 (28) will not be displaced apart. Therefore, operations such as assembly and disassembly of the roller 26 (28) are easy.

  The axial positioning of each retainer 30 (32) and each roller 26 (28) in the gear unit 12 is performed between the two retainers 30 (32) and the respective rollers between the ring plate 51 and the protrusion 48. In this embodiment, the axial length L1 (L2) of the protruding portion P1 (P2) of the coupling body 30C (32C) is the axial length of the roller 26 (28). Since the gap δ1 (δ2) is secured between the ring plate 51 and the protruding portion 48 as a result, the ring plate 51 and the protruding portion 48 and the protruding portion P1 (P2) are connected to each other. There is no interference.

  The retainer 30 and the retainer 32 are positioned in the axial direction when the adjacent second ring bodies 30B and 32B come into contact with each other. Such a positioning structure is likely to cause wear between the second ring bodies 30B and 32B. However, in this embodiment, the retainer 30 (32) is formed of a resin containing glass fibers. , Durability can be ensured satisfactorily. Further, in particular, the present embodiment is a configuration in which the adjacent second ring bodies 30B and 32B come into contact with each other to perform positioning in the axial direction of each other. Since the annular body overlaps on the entire circumference and the lubrication conditions are not good, the effect of being able to lubricate the roller 26 (28) satisfactorily by the configuration of the present embodiment is great.

  In this embodiment, the length L7 (L8) in the radial direction at the base end portion of the coupling body 30C (32C) adjacent to the first and second ring bodies 30A, 30B (32A, 32B) is the recess 60 ( 62) is set to be larger than the radial length L9 (L10), and on the outer peripheral side of the retainer 30 (32), the outside of the first and second ring bodies 30A, 30B (32A, 32B) Since the diameters d1, d2 (d3, d4) are the same as the outer diameter d5 (d6) of the coupling body 30C (32C), the strength of the retainer 30 (32) as a whole can be sufficiently maintained.

  Next, an example of another embodiment of the present invention will be described with reference to FIGS.

  The lengths (sizes) in the radial direction of the pair of ring bodies of the retainer according to the present invention are not necessarily the same. If it demonstrates with reference to the gear apparatus 12 of FIG. 1, there exists a merit which makes the length of a radial direction of a pair of ring body differ in the following cases, for example.

(A) When effective in relation to the position of the greasing port (or drain port):
In the case of the gear device 12 as shown in FIG. 1, the greasing port 50 is located near the retainer 32 on the flange body side. For this reason, for example, when paying attention to the retainer 30 on the non-flange body side, there is a request that the second ring body 30B wants to pass grease, but the first ring body 30A wants to keep grease (not want to pass). There is a request. Of course, the grease can enter from the side of the first ring body 30A of the retainer 30 on the side opposite to the flange body in a state of being enclosed in the space in the gear device 12, so this request is not an essential request. This is a request that functions effectively in terms of smooth filling of the lubricant. Accordingly, in response to this request, the radial length L11 (FIG. 2) of the first ring body 30A may be set longer than the radial length L13 of the second ring body 30B. Thereby, the blockage degree of the end part of the retainer 30 far from the greasing port 50 can be increased, and the grease sealed from the side of the retainer 32 close to the greasing port 50 is used for the rollers 26 and 28 of the two retainers 30 and 32. It is possible to stay more securely around the area.

(B) When effective in relation to the reduction ratio of the gear unit (the eccentric amount of the eccentric body):
When the reduction gear ratio of the gear device 12 is low, the eccentric amounts of the eccentric bodies 14 and 16 tend to increase. Therefore, when the lengths L13 and L14 in the radial direction between the second ring bodies 30B and 32B adjacent to each other are set longer than the lengths L11 and L12 in the radial direction of the first ring bodies 30A and 32A, respectively. Even if the amount of eccentricity is large, the adjacent second ring bodies 30B and 32B can be stably brought into contact with each other with a corresponding area.

(C) When valid in relation to the roller positioning member:
In an example such as the gear device 12, for example, in the retainer 32, the first ring body 32A side has a “member for positioning the roller 28” such as the ring plate 51, but the second ring body 32B. On the other side, there is no such positioning member. For this reason, compared with the radial length L12 of the first ring body 32A on the side where the positioning member of the roller 28 exists, the radial length L14 of the second ring body 32B on the side where the positioning member does not exist is set. It may be set longer. Thereby, both prevention of interference with the positioning member and securing of the strength of the retainer can be achieved at a higher level.

  Thus, the radial length of the ring body is determined by the position of the greasing port (whether the lubricant should be passed or fastened), the deceleration of the gear unit (the eccentric amount of the eccentric body), the positioning member of the roller In consideration of the presence or absence of the interference or the relationship with the strength required for the retainer itself, etc., the length may be set independently on each side.

  In the embodiment of FIGS. 7 and 8, the retainer 32 on the flange body side in the gear device 12 is replaced with a retainer 70 in consideration of the circumstances (B) and (C). The lengths L15 and L16 in the radial direction of the pair of first and second ring bodies 70A and 70B of the retainer 70 are set to different lengths (L15> L16).

  In this embodiment as well, a gap δ3 (corresponding to the gap δ1) is secured between the protruding portion P3 of the coupling body 70C and the protrusion 48 (only on the side where the ring plate 51 is provided).

  The retainer 70 is effective for replacing the retainer 32 on the flange body side of the previous embodiment, but may be replaced with the previous retainer 30 (inverted horizontally, that is, back-to-back). In this case, the above (C) can be satisfied, and the above (B), that is, a gear device having a large eccentricity can be more effective.

  Furthermore, for example, the retainer 32 may be left as it is, and only the retainer 30 may be replaced with the retainer 70 as it is (without being reversed horizontally). In this case, the roller is not pressed by the protrusion 48 but the end of the retainer 70 is pressed by a separate protrusion or the like. The combination of the retainer 32 and the retainer 70 functions particularly effectively for the request (A). In this way, the configuration in which the lengths in the radial direction of the first and second ring bodies are different from each other can be variously incorporated.

  About another structure, including the structure in which the recessed part 74 is formed in the axial direction center of 70 C of coupling bodies, it is the same as that of the retainer 30 (32) of previous embodiment.

  9 to 11 show an example of still another embodiment of the present invention.

  In the retainer 80 according to this embodiment, the outer diameter d11 of the connecting body 80C is set to be larger than the outer diameters d12 and d13 (d12 = d13 in this example) of the first and second ring bodies 80A and 80B. Has a protruding portion P4 that protrudes by Δ2 outwardly in the radial direction from the first and second ring bodies 80A, 80B.

  This is because the purpose of the present invention is to make it easier for the lubricant to enter the roller side beyond the ring body in the axial direction. Therefore, the passage of the lubricant (to the roller side) is not necessarily a ring. It is not necessary to exist inside the body in the radial direction, but based on the technical concept that it may exist outside the ring body in the radial direction. In particular, in the case where the introduction path 52 of the greasing port 50 is located on the radially outer side of the retainer, such as the gear device 12 as shown in FIG. There is a possibility that the grease that protrudes more radially outward than the second ring bodies 80A and 80B can more easily enter the roller side.

  In this embodiment, the retainer 80 includes the first and second ring bodies 80A and 80B, the connecting body 80C, and the protruding portion (the outer diameters 12 and d13 larger than the outer diameters 12 and d13 of the first and second ring bodies 80A and 80B). The portion including the diameter d11) is symmetrical with respect to the center plane C1 including P4 and the like, and the outer diameters d12 and d13, the inner diameters D12 and D13, and the radial lengths L15 and L16 are the same. Therefore, a symmetrical assembly is possible with respect to a member (not shown) for positioning the roller 82. In this embodiment also, the axial length L20 of the protruding portion (the portion having the outer diameter d11 larger than the outer diameters d12 and d13 of the first and second ring bodies 80A and 80B) P4 is equal to that of the roller 82. It is shorter than the axial length L21. In this embodiment, the positioning member of the roller 26 (28) positions the retainer 80 by pressing the outer peripheral portion of the roller 26 (28).

  A claw portion 80C1 that prevents the roller 82 from falling off radially outward is formed at the end portion on the outer peripheral side in the radial direction of the coupling body 80C. In this way, the claw portion for preventing the roller from falling off may be formed on either side of the connecting body in the radial direction, and if the roller can be fitted within the range of elastic deformation of the connecting body, both ends in the radial direction may be provided. It may be formed in the part. The claw portion need not be formed in the entire axial direction of the coupling body, and may be formed only in a part of the coupling body in the axial direction. This is the same as in the previous embodiment.

  In this embodiment, one recess 86 serving as a passage for the lubricating oil is formed along the circumferential direction on the inner peripheral side of the coupling body 80C. However, the recesses that serve as the passages for the lubricating oil may be formed on the outer peripheral side or may be formed on both sides as a matter of course. The number is not limited to one, and the size, shape, formation position, and the like are not particularly limited.

  In this embodiment (where the coupling body protrudes radially outward with respect to the ring body), the same modifications as in the previous embodiment are possible.

  In short, in the present invention, when the inner diameter of the connecting body is set smaller than the inner diameters of the first and second ring bodies as in the embodiment up to FIG. Since the corresponding grease is already secured on the inner peripheral side of the body, the relationship with the size of the connecting body on the outer peripheral side of the first and second ring bodies and the size of the first and second ring bodies are large and small. There is no particular limitation on how to set the relationship. The outer diameters of the first and second ring bodies may be set to be larger than the outer diameter of the coupling body, and the lengths (sizes) of the first and second ring bodies in the radial direction may be different. .

  On the other hand, when the outer diameter of the coupling body is set larger than the outer diameters of the first and second ring bodies as in the embodiment of FIGS. 9 to 11, the first and second ring bodies. Since the corresponding grease is already secured on the outer peripheral side of the first and second ring bodies, the relationship with the size of the connecting body on the inner peripheral side of the first and second ring bodies, and the magnitude relationship between the sizes of the first and second ring bodies. There is no particular limitation on how to set. The inner diameters of the first and second ring bodies may be set to be larger than the inner diameter of the coupling body, and the lengths (sizes) in the radial direction of the first and second ring bodies may be different.

  Of course, it is good also as a structure which a connection body protrudes in both radial direction inner side and an outer side with respect to a ring body.

DESCRIPTION OF SYMBOLS 12 ... Gear apparatus 14, 16 ... Eccentric body 18, 20 ... External gear 22 ... Internal gear 24 ... Input shaft 26, 28 ... Roller 30, 32 ... Retainer 30A, 30B, 32A, 32B ... 1st, 2nd ring Body 30C, 32C ... Connected body 30C1, 32C1 ... Claw part 30C2, 32C2 ... Base end part 34 ... Casing 36 ... Inner pin 38 ... Cross roller 42 ... Flange body 60, 62 ... Recess P1, P2 ... Projection part

Claims (14)

A retainer for holding a plurality of rollers,
A pair of ring bodies for positioning both end positions of each of the plurality of rollers;
With connecting the pair of ring members, and a connecting member for positioning the circumferential positions of the plurality of rollers, and the inner diameter of the coupling body is set smaller than the inner diameter of both the pair of ring members The roller retainer is characterized in that a radial length of the coupling body is larger than a radial length of both of the pair of ring bodies . In claim 1,
The roller retainer characterized in that an axial length of a portion of the connecting body, which has an inner diameter smaller than an inner diameter of the ring body, is shorter than an axial length of the roller. In claim 1 or 2,
The roller retainer , wherein an outer diameter of the connecting body is set to be equal to or smaller than an outer diameter of the ring body . A retainer for holding a plurality of rollers,
A pair of ring bodies for positioning both end positions of each of the plurality of rollers;
And a connecting body for connecting the pair of ring bodies and positioning circumferential positions of the plurality of rollers, and the outer diameter of the connecting body is larger than the outer diameters of both the pair of ring bodies. A roller retainer that is set and has a radial length of the coupling body larger than a radial length of both of the pair of ring bodies . In claim 4,
The roller retainer, wherein an axial length of a portion of the connecting body, which has an outer diameter larger than an outer diameter of the ring body, is shorter than an axial length of the roller. In claim 4 or 5,
The inner diameter of the coupling body, features and to Carlo over La retainer that it is set to more than the inner diameter of the ring body. In any one of Claims 1-6,
A retainer for a roller, wherein a claw portion for preventing the roller from dropping off is formed at an end portion in a radial direction of the coupling body. In claim 7,
The retainer of a roller, wherein the claw portion is formed only in a part of the coupling body in the axial direction. In any one of Claims 1-8,
The roller retainer is characterized in that a concave portion serving as a passage for the lubricant is formed along the circumferential direction in an axially intermediate portion of the connecting body. In any one of Claims 1-9 ,
A claw portion for preventing the roller from falling off is formed at one end portion in the radial direction of the coupling body,
A retainer for a roller, wherein a recess serving as a passage for a lubricant is formed along the circumferential direction at the other end portion in the radial direction of the coupling body .   In claim 10,
  The claw portion is formed at both axial end portions of the connecting body, and the concave portion is formed at an axial center portion of the connecting body.
  A roller retainer characterized by that. In any one of claims 1 to 11,
A roller retainer, wherein the pair of ring bodies have different radial lengths. A swinging intermeshing gear device in which an external gear that is swung and rotated by an eccentric body is inscribed in mesh with an internal gear,
The retainer according to any one of claims 1 to 12 is provided as a retainer that holds a plurality of rollers disposed between the eccentric body and the external gear. Gear device. In claim 13,
The eccentric body and the external gear are provided in a plurality of rows, and the plurality of rollers and a retainer for holding the roller are incorporated into the eccentric body and the external gear ,
While sliding the adjacent ring bodies of each retainer, the roller axial direction outer end surface is positioned by a positioning member,
The axial length of the protruding portion of the coupling body, which is an inner diameter smaller than the inner diameter of the ring body, is shorter than the axial length of the roller,
The swinging intermeshing gear device , wherein the protruding portion of the coupling body is shifted to the side opposite to the positioning member from the center of the roller .

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