JP3876105B2 - Internal gear structure with built-in casing and internal meshing planetary gear structure - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention is a casing built-in type comprising an internal gear that holds an external pin constituting an internal tooth by an external pin support member, and an internal gear casing that engages with the internal gear by its stepped portion. The internal gear structure of this invention, and the internal meshing planetary gear mechanism which employ | adopts this internal gear structure.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, internal gears that constitute internal teeth by a plurality of external pins are widely used in various mechanisms that transmit rotational power using gears.
[0003]
FIG. 5 shows a rotary drive device 30 including an intermeshing planetary gear mechanism 20 to which this type of internal gear 10 is applied, and a motor 22 connected thereto.
[0004]
The inscribed mesh planetary gear mechanism 20 is in a state in which it can rotate with respect to the first shaft 1 via the first shaft 1, the eccentric body 3 that rotates by the rotation of the first shaft 1, and the eccentric body 3. The external gear 5 to be incorporated, the internal gear 10 incorporated in the casing 12 and internally meshed with the external gear 5, and the second shaft connected to the external gear 5 so that only the rotation component thereof is transmitted. 2 is provided.
[0005]
That is, the intermeshing planetary gear mechanism 20 has a feature (a feature shown in International Patent Classification F16H1 / 32) that the center of the internal gear 10 is located inside the periphery of the external gear 5.
[0006]
Specifically, as shown in FIG. 6, the external gear 5 is loosely fitted to the eccentric body 3 by a bearing hole formed at the center thereof, and between the bearing hole and the eccentric body 3, A bearing roller 4 is inserted. Furthermore, a plurality of inner roller holes 6 are formed in the outer gear 5 in the circumferential direction, and an inner pin 7 and an inner roller 8 are loosely fitted therein. Further, outer teeth 9 having a trochoidal tooth shape or an arc tooth shape are provided on the outer periphery of the external gear 5 and are in mesh with the internal gear 10.
[0007]
Returning to FIG. 5, the inner roller 8 is held by the inner pin 7 in a rotatable state, and the base portion of the inner pin 7 is fitted into the flange portion 14 of the output shaft 2 in a fixed state. .
[0008]
The internal gear 10 has its own internal teeth formed by an external pin 11, and the external pin 11 is held in a freely slidable and rotatable state by the internal peripheral surface of the substantially cylindrical external pin support member 10. (Details will be described later).
[0009]
Next, the operation of this swinging intermeshing planetary gear mechanism 20 will be described.
[0010]
When the first shaft 1 rotates once, the eccentric body 3 rotates one time accordingly. The external gear 5 also tries to rotate by the rotation of the eccentric body 3, but its free rotation is restrained by the meshed state with the internal gear 10, and while meshing with the internal gear 10 (with slight rotation) ) Almost only rocking rotation.
[0011]
Specifically, for example, when the number of teeth of the external gear 5 is N and the number of teeth of the internal gear 10 is N + 1, the difference in the number of teeth is 1. Accordingly, every time the first shaft 1 rotates once, that is, every time the external gear 5 rotates by one swing, the external gear 5 is shifted by one tooth with respect to the internal gear 10 (slightly rotates). ). This means that the rotation of the external gear 5 has been reduced to -1 / N with respect to the rotation of the first shaft 1 (minus indicates reverse rotation).
[0012]
Such rotation of the external gear 5 (oscillation rotation with slight rotation) absorbs the oscillation component by the gap between the inner roller hole 6 and the inner roller 8, and only the rotation component is applied to the output shaft 2. Communicated. As a result, a reduction ratio of -1 / N is achieved between the first shaft 1 and the second shaft 2.
[0013]
As shown in FIG. 5, the first shaft 1 in the intermeshing planetary gear mechanism 20 is connected to a motor shaft 24 of a motor 22 (in this conventional example, integrated), and the motor 22 is used as a drive source as a whole. It functions as a reduction type geared motor.
[0014]
Next, the structure of the internal gear 10 will be described in more detail.
[0015]
As shown in an enlarged view in FIG. 7, the internal gear 10 is externally formed by a plurality of outer pins 11 constituting the inner teeth and a plurality of pin grooves 13 in the axial direction L formed on the inner peripheral surface 27 a of the inner gear 10. And an outer pin support member 27 that holds the pin 11 so as to be slidably rotatable.
[0016]
When viewed from the axial direction L, the pin groove 13 has a semicircular cross section. Accordingly, about half of the outer peripheral surface of the outer pin 11 held in the pin groove 13 is exposed to the inner side (center axis side). Naturally, this is because an internal tooth is formed by the exposed portion of the outer pin 11, and the external gear 5 (omitted in FIG. 7, see FIG. 6) meshes with the exposed portion.
[0017]
The two casings 12 disposed on both sides in the axial direction of the internal gear 10 have a ring-shaped first step portion 28 protruding in the axial direction, and a second step portion 29 having a smaller diameter than the first step portion 28. It is formed in steps. And the outer peripheral surface 28a of the 1st step part 28 is fitted with the inner peripheral surface 27a of the outer pin support member 27, and this casing 12 and the outer pin support member 27 (internal gear 10) mutually have a diameter. It is designed not to shift in the direction.
[0018]
Further, the outer peripheral surface 29 a of the second step portion 29 coincides with the inner peripheral circle formed by connecting the inner peripheral sides of the plurality of outer pins 11, that is, the tip circle of the inner teeth formed by the outer pins 11. ing. Therefore, both end sides of the outer pin 11 held in the pin groove 13 are located inside (this outer side) by the outer peripheral surface 29a of the second step portion 29 in a state where the first step portion 28 and the outer pin support member 27 are fitted. It is supported from the tooth tip side of the internal teeth composed of the pins 11. Further, the axial length of the outer pin 11 coincides with the distance S between the opposing surfaces 28b of the pair of first step portions 28. Therefore, the axial movement of the outer pin 11 is caused by this opposing surface 28b. Be regulated.
[0019]
In order to make the reduction ratio as high as possible, it is necessary to increase the number N of teeth of the internal gear 10 (the number of outer pins 11). Therefore, in this case, it is only necessary to increase the inner diameter of the outer pin support member 27 and to hold a large number of outer pins 11 by narrowing the interval between the pin grooves 13 as much as possible.
[0020]
In addition to the above structure, as shown in FIG. 8, a structure in which the outer periphery of the outer pin 111 is covered with a cylindrical outer roller 32 and inner teeth are formed by this outer peripheral surface (so-called outer roller type). There is also. This is because when the external gear (not shown) meshes, the outer roller 32 itself rotates smoothly, disperses and absorbs slip on the tooth surface, and reduces the rotational resistance of the external gear. This structure is widely used in places where high transmission efficiency is required.
[0021]
In this case, a roller groove 127b is formed in the circumferential direction on the inner circumferential surface 127a of the outer pin support member 127, and the outer roller 32 is prevented from contacting the inner circumferential surface 127a and the outer roller 32. It is designed to rotate smoothly. In addition, since it is as substantially the same as that of the prior art example already shown in FIGS. 5-7 about other structures etc., detailed description and the whole are carried out by making the last two digits the same numerals about the same or similar member and part. The illustration of is omitted.
[0022]
[Problems to be solved by the invention]
However, the casing 12 as shown in FIG. 7 has two step portions 28 and 29 formed therein, and its structure is very complicated. This serves to prevent one (first) step portion 28 from engaging with the internal gear 10 and relatively moving in the radial direction (so-called inlay role), and the other (second) step. This is because the stepped portion 29 needs to play a role of supporting the outer pin 11 forming the tooth surface and preventing the dropping. The same applies to the casing 122 shown in FIG.
[0023]
Furthermore, as a result of adopting the internal gear structure as described above, there has been a problem that the pin groove 13 formed in the outer pin support member 27 is not fully utilized throughout. That is, although the pin groove 13 is formed on the inner peripheral surface 27a up to both ends in the axial direction, the both end portions are actually inlays (specifically, engagement surfaces with the first step portion 28). ), There are wasted spaces S1 and S1 in the pin groove 13.
[0024]
The length S of the outer pin 11 is determined by the protruding amount in the axial direction of the external gear 5 (see FIG. 5) that meshes internally and the second step portion 29 that prevents the outer pin 11 from falling off. As a result, the internal gear 10 (outer pin support member 27) is elongated in the axial direction only by “useless portions S1, S1” (portions used by the spigot) of the pin groove 13. In particular, the inscribed mesh planetary gear mechanism 20 cited as the conventional example has a great merit in achieving a high reduction ratio in a compact state in the axial direction. .
[0025]
Furthermore, in the structure of the external gear 32 of the external roller 32 type as shown in FIG. 8, the force acting on the external roller 32 that meshes with the external gear is all supported by the shaft end portion S <b> 2 of the external pin 111. There must be. Therefore, it is necessary to lengthen the outer pin 111 to a certain extent and receive the force in a larger area. In addition to this, when the spigot portion S3 is required, the internal gear 110 is enlarged in the axial direction.
[0026]
Incidentally, it is considered that the internal gear 10 and the external gear 5 shown in FIG. 5 are actually meshed as shown in FIG. That is, as the external load of the rotary drive device 30 increases, the circumferential force acting on the outer pin 11 increases, resulting in elastic deformation of the outer pin support member 27, the second step portion 29 of the casing 12, and the like. In part, it is predicted that the outer pin 11 is slightly lifted from the pin groove 13. If it is operated for a long time in such a state, the outer pin 11 is fatigued and its life is likely to be shortened.
[0027]
The present invention has been made in view of the above problems, and an object of the present invention is to simplify the shape of the internal gear casing and to make the internal gear compact in the axial direction in the internal gear structure held by the casing. . Another object is to increase the allowable load of the internal gear in a compact state. Another object of the present invention is to apply an internal gear structure having such merits to an intermeshing oil gear mechanism.
[0028]
[Means for Solving the Problems]
The present invention includes an internal gear that holds a plurality of outer pins constituting an inner tooth by a plurality of axial pin grooves formed on an inner peripheral surface of a substantially cylindrical outer pin support member, and an own gear. An internal gear casing comprising an internal gear casing that engages an internal gear with a ring-shaped stepped portion to restrict relative radial displacement, and an internal gear casing The above-mentioned object is achieved by configuring the step portion so that it also serves to support the plurality of outer pins of the internal gear from the inside by its outer peripheral surface.
[0029]
In this way, since the outer pin is supported only by (one) step portion that restricts the relative deviation from the internal gear, it is necessary to form a step portion exclusively for supporting the outer pin. In addition, the structure of the internal tooth casing is simplified.
[0030]
The internal tooth casing includes any member having the above-described configuration. Therefore, in addition to the casing that houses the speed increase / reduction gear having the internal gear, a casing that rotates integrally with the internal gear (as part of a so-called internal gear) is also included.
[0031]
Specifically, in the vicinity of the axial end portion on the inner peripheral surface of the outer pin support member, a protrusion having a tip coincident with an inner peripheral circle formed continuously to the inner peripheral side of the plurality of outer pins is provided in the radial direction. What is necessary is just to make it protrude inside and to make the front-end | tip of this protrusion part engage with the step part of the casing for internal teeth.
[0032]
If the outer pin support member and the stepped portion of the inner tooth casing are engaged with each other, the mutual radial displacement is restricted. A structure was adopted in which a protrusion was formed and the tip of the protrusion was made to coincide with an inner circumference formed by connecting the inner peripheral side of the outer pin.
[0033]
In this case, when the stepped portion engages with the protruding portion to restrict the radial displacement of the outer pin support member, the stepped portion is positioned so that it can naturally support the outer pin from the inside. Will do. As a result, it is not necessary to form a “dedicated” step portion to prevent the outer pin from falling off, and the structure of the internal tooth casing is simplified. In addition, since the protrusion is disposed in the vicinity of the end in the axial direction of the inner peripheral surface of the outer pin support member, for example, when the tooth surface of the inner tooth is formed by exposing about half of the outer pin, Even when the outer pin is further covered with a cylindrical outer roller, the protrusion does not get in the way.
[0034]
Note that the fact that the tip of the protrusion is `` matched '' to the inner circumference circle is not limited to the case where it completely matches, but to the extent that this step can support the outer pin from the inner circumference side, That is, the case where the object of the present invention can be achieved is included. That is, even if a minute gap is formed between the outer pin and the step portion so that the outer pin can freely rotate within the pin groove, it is within the scope of the present invention.
[0035]
By the way, when employ | adopting the structure of the said invention, it is preferable to match the both ends of an outer pin with the both sides | surfaces of an outer pin support member.
[0036]
In this way, since the outer pin can be held using the entire axial length of the outer pin support member, a useless space (a space not holding the outer pin) does not occur in the pin groove ( Or decrease). Therefore, especially when the internal gear is of the outer roller type, the holding area of the outer pin supporting the outer roller by the pin groove can be increased. The load can be increased. On the other hand, considering the case where the length of the outer pin is constant, the width (axial length) of the outer pin support member (internal gear) can be relatively reduced as compared with the conventional case.
[0037]
The present invention is not limited to the case where the protrusion is formed over the entire circumferential direction of the inner peripheral surface of the outer pin support member, and the protrusion and the step portion are displaced from each other in the radial direction. It is preferable to form with a reasonable arrangement shape to the extent that it is regulated.
[0038]
In order to further increase the allowable load, the protrusion is formed between a pair of outer pins adjacent to each other in the circumferential direction, and the surface on the outer pin side of the protrusion is placed close to the outer peripheral surface of the outer pin. It is also desirable that the outer pin be configured to be able to apply a reaction force to the circumferential force received when meshing with the other external gear.
[0039]
In this way, compared to the conventional case where the outer pin is held only by a pin groove having a semi-circular cross section, the protrusion also serves as a so-called circumferential stopper (regulating member). The outer pin is always held in the pin groove in a stable state against the load.
[0040]
The outer pin according to the present invention is not limited to the case where the tooth surface of the inner teeth is formed by the outer peripheral surface of the outer pin, and the outer periphery of the outer pin is covered with a substantially cylindrical outer roller. Also included are those in which the tooth surface is constituted by the outer peripheral surface of the outer roller (so-called outer roller type). In this case, the outer pin is still part of the inner tooth.
[0041]
Furthermore, in these inventions, a recess for allowing the mating external gear to be incorporated into and removed from the internal gear in the axial direction is provided radially outward along the axial direction of the protrusion. It is preferable. In particular, when the difference in the number of teeth relative to the counterpart external gear is small (for example, a swinging intermeshing planetary gear mechanism), the tip circle of the counterpart external gear interferes with the tip circle of the internal gear. In some cases (that is, when the tooth tip circle diameter of the external gear is larger than the tooth tip circle diameter of the internal gear), the protruding portion becomes an obstacle when the external gear is assembled and taken out in the axial direction. There is a possibility, but if this recess is used, it can be easily incorporated. The shape and arrangement of the recess may be determined as appropriate in consideration of the shape and size of the mating external gear.
[0042]
In consideration of the above-described configuration of the present invention, this internal gear structure is preferably applied to the following intermeshing planetary gear mechanism. Specifically, a first shaft, an eccentric body that rotates by the rotation of the first shaft, an external gear that is incorporated so as to be eccentrically rotatable with respect to the first shaft via the eccentric body, and an internal tooth An internal gear that is incorporated in a casing for internal engagement with the external gear, and a second shaft that is coupled to the external gear so that only the rotation component of the external gear is transmitted. In the meshing planetary gear mechanism, the internal gear structure according to the above-described invention may be employed for the internal gear incorporated in the internal gear casing.
[0043]
In this way, the axial dimension can be shortened, the casing structure can be simplified, and the manufacturing cost can be reduced.
[0044]
DETAILED DESCRIPTION OF THE INVENTION
DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
[0045]
FIG. 1 shows a rotary drive device 230 including an intermeshing planetary gear mechanism 220 according to the first embodiment of the present invention. This rotation drive device 230 functions as a geared motor as a whole by connecting the first shaft 201 of the intermeshing planetary gear mechanism 220 to the motor shaft 224 of the motor 222.
[0046]
Except for the internal gear structure, which will be described in detail later, the configuration is almost the same as that of the conventional rotary drive device 30 shown in FIG. 6 and the like. The same reference numerals as those of the rotation drive device 30 are assigned to the last two digits, so that the redundant description of the configuration and operation of the rotation drive device 230 is omitted.
[0047]
The intermeshing planetary gear mechanism 220 includes a first shaft 201, an eccentric body 203 that rotates by the rotation of the first shaft 201, and a state that can eccentrically rotate with respect to the first shaft 201 via the eccentric body 203. , The internal gear 210 incorporated in the casing 212 (corresponding to the internal gear casing in the present invention) and in mesh with the external gear 205, and only the rotation component of the external gear 205. And a second shaft 202 coupled to the external gear 205 so as to transmit.
[0048]
As shown in an enlarged view in FIG. 2, the internal gear 210 includes a plurality of axial pins formed on the inner peripheral surface 227 a of the substantially cylindrical outer pin support member 227. It is held by the pin groove 213.
[0049]
In the vicinity of both ends in the axial direction L of the inner peripheral surface 227a of the outer pin support member 227, a protruding portion 250 protruding inward in the radial direction is formed, and the tip 250a of the protruding portion 250 is connected to the inner side of the outer pin 211. It coincides with an inner circumferential circle formed by connecting the circumferential sides (in this embodiment, a tip circle of an internal tooth). The protrusions 250 are formed between a pair of outer pins 211 adjacent in the circumferential direction (between adjacent pin grooves 213), and both ends of each outer pin 211 in the axial direction are outer pin support members 227. Reaches both ends (both sides) in the axial direction.
[0050]
Further, the protrusion 250 is disposed close to the outer peripheral surface (in the vicinity of the shaft end) of the outer pin 211, whereby the surface 250 b on the outer pin 211 side of the protrusion 250 acts on the outer pin 211. A reaction force can be applied to the circumferential force.
[0051]
On the other hand, the casing 212 in which the internal gear 210 is incorporated is formed with only one substantially ring-shaped step 228 that protrudes in the axial direction L and toward the internal gear 210 (in the present invention, there is only one). Not limited to). The step portion 228 (specifically, the outer peripheral surface 228a of the step portion 228) is engaged with the tip 250a of the projection portion 250, whereby the casing 212 and the internal gear 210 are displaced from each other in the radial direction. The outer pin 211 is supported from the inside. That is, one step portion 228 serves as a so-called inlay role and a role to support the outer pin 211.
[0052]
According to the “casing built-in internal gear structure” described above, it is not necessary to form two or more steps in the casing as in the conventional internal gear structure shown in FIG. The structure can be simplified and the manufacturing cost can be reduced.
[0053]
Further, the outer pin 211 can be held using the entire pin groove 213 formed in the outer pin support member 227. In other words, the length of the outer pin 211 can be extended compared to the conventional case. Therefore, since the outer pin 211 is held in a wide area, the allowable load of the internal gear 210 is increased. On the other hand, when it is not necessary to extend the outer pin 211, the outer pin support member 227 can be shortened in the axial direction, and as a result, the rotation drive device 230 (internal meshing planetary gear mechanism 220). Becomes shorter in the axial direction. In addition, since both ends of the outer pin 211 coincide with both side surfaces of the outer pin support member 227, the axial movement can be restricted by the casing 212.
[0054]
Further, even when a large force is applied in the circumferential direction when the outer pin 211 of the internal gear 210 is engaged with the external gear 205, the protrusion 250 is added to the force in addition to the pin groove 213. I can resist. As a result, even when a large load is applied to the outer pin 211, the pin 211 can be held stably and stably throughout the pin groove 213, and fatigue of the outer pin 211, the pin groove 213, etc. is reduced. Life is extended.
[0055]
Next, with reference to FIG. 3, a description will be given of a rotation drive device 330 that employs an internal gear structure according to a second embodiment of the present invention. The rotational drive device 330 is the same as the rotational drive device 30 shown in the conventional example except for the portions related to the present invention. Thus, the detailed description and the entire illustration are omitted, and the main part will be described in detail.
[0056]
FIG. 3 is an enlarged view of a casing built-in type internal gear structure in the rotation drive device 330. An outer roller 332 is coated on the outer periphery of the outer pin 311 in this internal gear structure, and an outer surface of the outer roller 332 forms an inner tooth surface. Therefore, as shown in the conventional example, a roller groove 327b is formed in the circumferential direction on the inner peripheral surface 327a of the outer pin support member 327 so that the outer roller 332 rotates smoothly.
[0057]
In the vicinity of both ends in the axial direction L of the inner peripheral surface 327a of the outer pin support member 327, a protruding portion 350 protruding radially inward is formed, and the tip 350a of the protruding portion 350 passes the outer pin 311 inside. It is coincident with the inner circumference circle (for internal tooth tips) formed in a row.
[0058]
The protrusion 350 is formed between a pair of outer pins 311 adjacent in the circumferential direction (between adjacent pin grooves 313). As a result (because the protrusion 350 does not get in the way), the outer pin 311 The axial ends of the outer pin support members 327 reach both ends (both side surfaces) in the axial direction.
[0059]
Further, the protrusion 350 is disposed close to the outer peripheral surface of the outer pin 311 (in the vicinity of the shaft end), whereby the outer pin 311 receives a surface 350b on the outer pin 311 side of the protrusion 350. It is possible to apply a reaction force to the directional force.
[0060]
As shown in FIG. 4, in the second embodiment, the external gear 305 is moved in the axial direction (apart from the pin groove 313) along the axial direction of the plurality of protrusions 350 formed in the circumferential direction. A concave portion 352 for enabling assembling / removing is provided in a radially outward direction. This includes the concept of arranging the protruding portion 350 so as to form the concave portion 352 and determining the shape of the protruding portion 350.
[0061]
On the other hand, the casing 312 in which the internal gear 310 is incorporated is formed with only one substantially ring-shaped step 328 protruding in the axial direction L and toward the internal gear 310. Since this step portion 328 (specifically, the outer peripheral surface 328a of the step portion 328) is engaged with the tip 350a of the projection portion 350, the radial displacement between the casing 312 and the internal gear 310 is restricted. In addition, the outer pin 311 is supported from the inside. That is, one step portion 328 serves as a so-called inlay role and a role to support the outer pin 311.
[0062]
Therefore, according to the second embodiment, in addition to the effects of the first embodiment, the tip circle of the external gear 305 meshing with the internal gear 310 is connected to the inner circumference of the outer pin 311. The outer gear 305 can be easily incorporated into and taken out from the internal gear 310 in the axial direction by using the recess 352 even when approaching or larger than the inner circumference. . As a result, gear assembly, maintenance, and the like are facilitated.
[0063]
In view of the above, the shape / arrangement of the protrusions 350 may be appropriately set in consideration of the shape / size, etc. of the external gear 305. Generally, as shown in FIG. Preferably, a pair of protrusions 350 are formed in the circumferential direction between a pair of adjacent outer pins 311, and a recess 352 is formed between the pair of protrusions 350.
[0064]
In particular, in the case of the internal gear 310 of the outer roller type, it is necessary to receive all the force acting on the tooth surface (outer roller 332) at the shaft end portions S10 and S10 of the outer pin 311. As a result of the extension of the shaft end portions S10 and S10, the allowable load of the internal gear 310 increases (without increasing the gear size).
[0065]
In the above-described embodiment, the case where the protrusions are formed between “all” of the plurality of outer pins is shown. However, the present invention is not limited to this, and can serve as a so-called inlay. What is necessary is just to form a protrusion part reasonably, and what is necessary is just to set the shape of a protrusion part suitably in the range which can achieve the objective of this invention.
[0066]
Moreover, it is not limited to the case where the internal gear is incorporated so as to be sandwiched between two casings, and the internal gear may be incorporated in one casing. Accordingly, the protrusions are not limited to the case where they are formed at both ends in the axial direction of the outer pin support member as in this embodiment, and may be formed only on one side.
[0067]
Further, the internal gear structure of the casing built-in type is not limited to the application to the intermeshing planetary gear mechanism, and can be widely used for general reduction gears, speed-up gears, and the like. Furthermore, in addition to the case where the casing (for internal teeth) and the internal gear become “fixing elements” as in the present embodiment, they rotate together to input / output rotational power. You may comprise so that it may do. That is, the “inner gear casing” in the present invention is intended to be integrated with the internal gear, and is not limited to a gear box or the like generally referred to.
[0068]
【The invention's effect】
According to the present invention, the shape of the internal gear casing is simplified, and the axial length of the internal gear structure is shortened. Further, since the length of the outer pin can be made relatively longer than that of the outer pin support member, the allowable load of the internal gear increases.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a rotary drive device employing an intermeshing planetary gear mechanism according to a first embodiment of the present invention.
FIG. 2 is a partially enlarged perspective view showing a casing built-in type internal gear structure in the rotation driving device.
FIG. 3 is a partially enlarged perspective view showing a casing built-in type internal gear structure according to a second embodiment of the present invention.
FIG. 4 is a sectional view showing a state in which an external gear is incorporated in the internal gear structure.
FIG. 5 is a cross-sectional view showing a rotary drive device adopting a conventional intermeshing planetary gear mechanism;
6 is a sectional view taken along line VI-VI in FIG.
FIG. 7 is a partially enlarged perspective view showing a casing built-in type internal gear structure in the rotation driving device.
FIG. 8 is a partially enlarged perspective view showing an outer roller type internal gear structure.
FIG. 9 is a partially enlarged view schematically showing the meshing state of the internal gear in the rotation drive device.
[Explanation of symbols]
201 ... 1st axis
202 ... 2nd axis
203 ... eccentric body
205, 305 ... external gear
207 ... Inner pin
210, 310 ... Internal gear
211, 311 ... outer pin
212, 312 ... casing
214 ... Career
220 ... Internal mesh planetary gear mechanism
222: Motor
227, 327 ... outer pin support member
227a, 327a ... inner peripheral surface
228, 328 ... Stepped portion
230, 330 ... Rotation drive device
250, 350 ... protrusion
250a, 350a ... tip
332 ... Outer roller

Claims (7)

An internal gear that holds a plurality of outer pins constituting the inner teeth by a plurality of axial pin grooves formed on the inner peripheral surface of a substantially cylindrical outer pin support member, and a substantially ring-shaped step that the inner gear has. A casing built-in type internal gear structure comprising: an internal gear casing that restricts a relative radial shift by engaging a portion with the internal gear;
The casing built-in type characterized in that the step portion of the casing for internal teeth is configured to support the plurality of outer pins of the internal gear from the inside by an outer peripheral surface of the casing. Tooth gear structure. In claim 1,
Protrusions whose tips coincide with the inner circumference formed by connecting the inner circumference sides of the plurality of outer pins in the vicinity of the axial ends on the inner circumference of the outer pin support member protrude radially inward. As it forms,
A casing built-in type internal gear structure characterized in that the tip of the projection is engaged with the step of the casing for internal teeth. In claim 2,
A casing built-in type internal gear structure characterized in that both ends of the outer pin in the axial direction coincide with both side surfaces of the outer pin support member. In claim 2 or 3,
The protrusion is formed between a pair of outer pins adjacent to each other in the circumferential direction and is brought close to the outer peripheral surface of the outer pin. A built-in casing internal gear structure characterized in that a reaction force can be applied to the circumferential force received when meshing with the casing. In claim 2, 3 or 4,
A casing built-in type internal gear structure characterized in that a cylindrical outer roller is covered on an outer periphery of the outer pin, and a tooth surface is constituted by the outer peripheral surface of the outer roller. In any of claims 2 to 5,
A recess for enabling the external gear to be assembled and removed from the axial direction with respect to the internal gear is provided radially outward along the axial direction of the protrusion. A built-in casing internal gear structure. A first shaft, an eccentric body that rotates by the rotation of the first shaft, an external gear that is incorporated so as to be eccentrically rotatable with respect to the first shaft via the eccentric body, and an internal gear casing. An internal meshing planetary gear mechanism comprising: an internal gear that internally meshes with the external gear; and a second shaft that is coupled to the external gear so that only the rotation component of the external gear is transmitted. In
An internal meshing planetary gear mechanism in which the internal gear structure according to any one of claims 1 to 6 is adopted for the internal gear incorporated in the internal gear casing.

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