JPH0874946A - Planetary gear device - Google Patents

Abstract

PURPOSE: To simplify a structure and to shorten a dimension in the axial direction by freely rotationally journalling a sun gear in each rear planet gear shifting unit to a supporting shaft concentrically projected on the output side end face of an input shaft in a planetary gear device in which plural planet gear shifting units are built in a housing member. CONSTITUTION: In a planetary gear device 1 serving as a flange type gear motor having an electric motor M, three stages or more of planet gear shifting units individually consisting of a sun gear 2, an annulus 3, and a planet carrier body 6, in which planet gears 5 are integrally built in a carrier 4 freely rotationally, are built in a housing member 7. A sun gear 2i in a planet gear shifting unit Ui is arranged in an input shaft 11, while each of sun gears 2m, 2o of the rest of the planet gear shifting units Um, Uo heading for an output shaft 12 is arranged integrally with the planet carrier body 6 of the adjacent planet gear shifting unit. In addition, the planet carrier body 6 in the planet gear shifting unit Uo in the last stage is fixed in the output shaft 12, and the sun gear 2 is journalled to a supporting shaft 18 integrally with the output shaft 12.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is constructed by pivotally supporting the sun gears of the planetary gears located on the output side of the planetary gears on the input side on a support shaft provided on the input shaft and the output shaft. , The present invention relates to a planetary gear device that can be easily configured and can reduce the axial size.

[0002]

2. Description of the Related Art An internal gear type planetary gear device using a sun gear, an internal gear, and a planetary gear that is rotatably supported by a carrier is well known and is often used as a speed change mechanism for deceleration and acceleration.

However, in the planetary gear device, the carrier that pivotally supports the planetary gear that revolves while revolving while simultaneously meshing with the sun gear and the internal gear, correctly holds the center of rotation of the carrier concentrically with the sun gear and the internal gear. It is a prerequisite to be done.

Therefore, for example, Japanese Patent Laid-Open No. 5-24031
As shown in FIG. 6, as disclosed in Japanese Patent Publication No. 5, the carrier A is supported by a ball bearing C arranged on the outer periphery of the carrier, and as disclosed in Japanese Patent Publication No. 59-30938, FIG. As shown in, the planetary gear D
, A planet ring E of the same diameter as the pitch circle is arranged side by side,
It is known that the planet ring E is rolled by the outer ring F.

On the other hand, there are planetary gear devices having a large capacity to a small capacity of about 0.2 kW or less. Particularly, for small capacity devices, cost reduction and size reduction are desired.

[0006]

However, in the former case shown in FIG. 6, the outer circumference of the carrier is generally large in diameter, and the ball bearing C also becomes large in size to increase the cost. Since the width and outer diameter are also large, the axial dimension and outer diameter dimension of the device tend to be large.

In the latter of FIG. 7, the planet ring E increases the number of parts, increases the number of assembling steps, and raises the cost, and the size in the axial direction is large, and the planet ring E is the planet gear D. Therefore, it is difficult to maintain the concentricity when the number of planetary gears D is small.

According to the present invention, the sun gear is rotatably supported by the support shaft projecting between the input shaft and the output shaft, and the carrier is concentrically held by the support shaft. The purpose of the present invention is to provide a planetary gear device that can be used.

[0009]

The present invention comprises a sun gear and
A housing member is provided with a plurality of planetary gears including an internal gear that surrounds the sun gear and a planet carrier body that rotatably and integrally supports the sun gear and a planet gear that meshes with the internal gear between a pair of carriers. A planetary gear device to be incorporated,
The input shaft is provided with a sun gear of the planetary gear stage on the input side, and each sun gear of the planetary gear stage after going to the output shaft is integrated with the planet carrier body of the planetary gear stage adjacent on each input side,
While fixing the planet carrier body of the most planetary gear stage to the output shaft, project the sun gear of each of the succeeding planetary gear stages concentrically with the output side end face of the input shaft or the input side end face of the output shaft. The planetary gear device is characterized in that it is rotatably supported on an established support shaft.

According to a second aspect of the present invention, the sun gear of the next planetary gear next adjacent to the planetary gear of the input side is arranged next to the sun gear of the output side end face of the input shaft, and the planetary gear of the most gear stage. The sun gear is rotatably supported by a support shaft on the input side end surface of the output shaft.

[0011]

The sun gear of the subsequent planetary gear stage is fixed concentrically with the planet carrier body of the planetary gear stage adjacent to the input side of the sun gear, and the sun gear is provided concentrically on the input and output shafts. Since they are pivotally supported on the shaft, each planet carrier is held concentrically with the support shaft through the sun gear at the next stage to which the planet carrier is fixed, resulting in a reduction in radial eccentricity and support. By making them uniform, the precision of meshing between gears can be improved and noise can be reduced.

Further, by reducing the eccentricity, it is possible to improve the load distribution ratio in the planetary gear, reduce vibration, and suppress uneven wear to extend the life of the gear and the device. In addition, the improvement of the distribution ratio of load can reduce the margin ratio to the tooth width, and it is possible to reduce the cost by downsizing the tooth width and downsizing, and also to reduce the cost and downsizing by not using a large bearing or planet ring. Becomes

[0013]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. 1 to 5, a planetary gear device 1 includes a sun gear 2
And one or more planetary gear stages U including an internal gear 3 and a planetary carrier body 6 in which a planetary gear 5 is rotatably and integrally incorporated in a carrier 4 are incorporated in a housing member 7.
And a support shaft 8 concentrically provided on the input shaft 11 or the output shaft 12
The sun gears 2 of the rear planetary gear stage U, which are fixed to the planet carrier body 6, are pivotally supported on the upper side. As a result, the planet carrier bodies 6 of the subsequent planetary gear stage U are held concentrically with the input shaft 11.

In the present embodiment, the internal gear 3 uses a punched laminate in which a plurality of press punched plates 9 ... Punched by fine blanking are stacked.
In addition, the planetary gear device 1 is formed as a flange type gear motor having the electric motor M in this embodiment.

Further, in this example, the planetary gear stage U has three planetary gear stages Ui, Um, Uo (i,
m and o are used as necessary when distinguishing the input stage, the intermediate stage, and the output stage. The same shall apply hereinafter), and the planetary gear stage U of the input stage
i is the rotor shaft of the electric motor M, that is, the sun gear 2i formed at the tip of the input shaft 11 of the planetary gear device 1, and the internal gear 3i supported by the housing member 7 and surrounding the sun gear 2i.
, And an integral planet carrier body 6 in which planetary gears 5i are pivotally supported on the plurality of support shafts 22 between the two carriers 4iA and 4iB that are coupled by the coupling shafts 21 ...
i and.

The intermediate planetary gear stage Um, which is the next planetary gear stage adjacent to the input side planetary gear stage Ui on the output side.
Is a sun gear 2m, an internal gear 3m supported by the housing member 7 and surrounding the sun gear 2m, and two carriers 4m.
Like the input stage, A and 4 mB are composed of an integral planet carrier body 6 m in which a planet gear 5 m is rotatably supported. The sun gear 2m of the next planetary gear stage adjacent to the output side to the planetary gear stage Ui on the input side, that is, the sun gear 2m of the intermediate planetary gear stage Um is the planetary gear stage adjacent to the input side, that is, the planet of the input stage. It is fixed to the carrier 4iB on the output side of the planet carrier 6i of the gear Ui. Further, in this embodiment, the sun gear 2m is pivotally supported on the support shaft 8A provided on the output end surface of the input shaft 11.

Further, the planetary gear stage U which is adjacent to the intermediate planetary gear stage Um on the output side, that is, the output stage in this example,
Therefore, the planetary gear stage Uo, which is also the final stage, is the sun gear 2o.
And an internal gear 3o that is supported by the housing member 7 and surrounds the sun gear 2o, and a planet carrier body 6o that similarly rotatably supports the planet gears 5o between the two carriers 4oA and 4oB. . Further, the sun gear 2o is concentrically fixed by the carrier 4mB on the output side of the planet carrier body 6m of the planetary gear stage Um of the intermediate stage which is adjacent on the input side. Further, the carrier 4oB on the output side is fixed to the rear end of the output shaft 12. In the present embodiment, the sun gear 2o is provided on the input end surface of the output shaft 12 as the support shaft 8 described above.
It is pivoted to B.

Each of the support shafts 22 has a cylindrical bearing 3
5. The planetary gears 5i, 5m, and 5o are rotatably supported by interposing 5, thrust bearings 36 and 36 (only shown in FIG. 1).

The planetary gear unit 1 has two planetary gears U.
In the case of the above, it may be supported by either the support shaft 8A of the input shaft 11 or the support shaft 8B of the output shaft 12, and it is preferable to select one having a smaller relative rotational speed. It should be noted that when four or more planetary gears U are used, the same judgment is made.

The housing member 7 is inserted into the insertion portion 24 in which a cylindrical motor housing Hm having a bottom and surrounding the stator of the electric motor M extends beyond the stator. The bracket B1 on the input side and the bracket B2 on the output side fitted at the front end of the insertion portion 21 are formed. Further, in the insertion portion 24, between the brackets B1 and B2 on the input and output sides, the internal gear 3i is inserted from the input side.
, The first spacer 13A, the internal gear 3m, the second spacer 13B, and the internal gear 3o are arranged side by side next to each other.

The insertion portion 24 is capable of accommodating the planetary gear stage U and has a step 25 for positioning the internal gear 3i by being formed to have a diameter slightly larger than that of a portion accommodating the stator. The bracket B1 on the input side
Bearing b1 and the bearing b2 on the rear wall of the motor housing Hm
And the input shaft 11, that is, the sun gear 2i, by the insertion portion 2
It is supported concentrically with 4. Output side bracket B2
As shown in FIG. 2, an outer cylinder portion 28 fitted and fixed to the insertion portion 24 is attached to a flange 27 having mounting holes at four corners.
And an inner cylindrical portion 29 that supports the output shaft 12 by bearings b3 and b4 concentrically with the insertion portion 24, and thus concentrically with the input shaft 11 and its sun gear 2i. The input shaft 11,
The output shaft 12 is sealed by seals S1 and S2. The housing member 7 and the output-side bracket B2 may be fixed by press fitting, or may be fixed by using an appropriate fixing tool such as a bolt or a screw 43 as shown in FIG. Further, the motor housing Hm has a length for forming the electric motor M, and can be separably connectable with a housing member for accommodating the planetary speed stage U.

In this example, the internal gears 3i, 3m, 3o are made of the punched laminate of the press punched plates 9 as described above,
The press punching plate 9 is formed by punching a metal plate by fine blanking. As shown in FIGS. 4 and 5, the press punched plate 9 has an inner peripheral surface 9a having an inner tooth portion 3A and a tip circle of the inner tooth portion 3A, and a concentric outer periphery having a concave groove 31 for checking the alignment position. A recess 1 formed in a ring shape by punching the surface 9b and provided on one surface
0A and a convex portion 10B which can be fitted into the concave portion 10A and which is provided on the other surface, form a phase matching fitting portion 10.

As is well known, the fine blanking process is performed in 1923 by the Swiss Fritz system.
Proposed by Mr. Schicess), which has a plate presser and a reverse presser, and uses a punch die with extremely small clearance to apply compressive force to the plate material to increase ductility and suppress the occurrence of fracture surface due to cracking. This is a method, and when the metal plate is a thin plate, paying attention to the fact that the cut surface is particularly beautiful and highly accurate, by stacking thin press-punched plates 9 ... to form a punched laminate, it is inexpensive and can be used. The precision internal gear 3 can be manufactured. The plate thickness of the press punched plate 9 is 1.5 to
A plate material made of an alloy steel such as chrome molybdenum steel having excellent strength and toughness, which is about 3.5 mm, about 2.2 to 2.8 mm in this example, can be preferably used.

The outer diameter of the outer peripheral surface 9b is 50 to 120 mm.
The internal tooth portion 3A of the inner peripheral surface 9a has a module of about 0.5 to 1.25. Since the punching accuracy is improved as the plate thickness is reduced, it is possible to punch a small module. It was confirmed that about 0.7 mm module is possible when the plate thickness is about 2.5 mm.

As described above, when the punching laminate precision punched by fine blanking is used as the internal gear 3, the production can be made efficient, the cost can be reduced, and the quality is stabilized. Further, the punching can be performed with high accuracy, the accuracy of the tooth portion can be improved, and the strength of the internal gear 3 can be adjusted by changing the number of stacked sheets according to the required strength. Also press punched plate 9
Since it has a ring shape consisting of ..., The rigidity in the radial direction is reduced as compared with the case of an integrated product having the same thickness, the flexibility in the radial direction is increased, and the tooth contact is also improved.

Further, the phase matching fitting portion 10 of the press punched plate 9 has a recess 10A on one surface and the recess 10A.
It has a shape that fits into A, for example, a concave portion 10A and a convex portion 10B on the other surface of the same shape, and is formed in association with the tooth phase of the internal tooth portion 3A. That is, if the concave portion 10A and the convex portion 10B are at the same position on the front and back sides, the concave portion 10A of the adjacent press-punched plate 9 is
By fitting the convex portions 10B with the convex portions 10B, the tooth traces of the internal tooth portions 3A of all the press punched plates 9 can be aligned and aligned in the axial direction correctly. When the concave portion 10A and the convex portion 10B have the same position and shape on the front and back, they can be formed by half-pressing the press.

Further, in the phase matching fitting portion 10, the angles sandwiching the radial line are unequal angles, for example, 150 °, 120 °, 9
It is provided on the radius line which is 0 °. Note that only one angle may differ from the other angles. As a result, fitting is always performed only at a fixed position, facilitating manual work or automatic mechanical assembly, and eliminating fitting error.

Further, the concave portion 10A on the outer side surface of the press punching plate 9 on the input side of the internal gear 3i is fitted to the convex portion 10C provided on the first bracket B1. Each internal gear 3i, 3
First and second spacers 13A and 13 adjacent to m and 3o
Similarly, concave portions 10C or convex portions 10D are similarly provided on the surfaces of the output side bracket B2 facing each other, and they are sequentially fitted to each other.

As a result, the internal gear 3, the spacer 13, and the brackets B1 and B2 have convex portions and concave portions 10A to 10A on adjacent surfaces.
The 10Ds are fitted to each other and are prevented from rotating as a whole to be integrated with each other to prevent relative positional displacement in the circumferential and radial directions.

As long as the projections and recesses can be fitted, various shapes such as a so-called circular shape and a non-circular shape such as a square shape can be adopted. Spacers 13A, 13B, bracket B
It is also possible that all of 1, 1, B2, etc. form a recess, and when the recesses of the internal gear 3 face each other, they are joined by a positioning pin (not shown) that fits in both recesses.

Further, in the present example, the concave grooves 31 are provided at two positions on the outer peripheral surface on a diagonal line, and the concave grooves 31 are used not only for phase alignment but also, for example, in a bracket (not shown). ) Can be used for the integration of the punched laminated body such as by inserting in the longitudinal direction.

The support shaft 8 is a pin-shaped body composed of a support shaft 8A projecting from the output side end face of the input shaft 11 and a support shaft 8B projecting from the input side end face of the output shaft 12, and the insertion and attachment thereof. It can rotate concentrically with the internal gears 3i, 3m, 3o arranged in the portion 24.

On the other hand, the sun gears 2m, 2o of the planetary gear stages Um, Uo of the intermediate stage and the output stage (that is, the final stage) are, in this example,
Each has a stepped cylindrical piece shape consisting of a tooth portion 2A and a small-diameter portion 2B which is smaller in diameter than the tooth portion 2A and is integral with each other, and each has a through hole coaxial with the tooth portion 2A at the center thereof. There is.

The output side carriers 4iB, 4mB of the planet carrier bodies 6i, 6m each have a boss portion 39 projecting toward the output side at the center thereof, and the center holes of the boss portions 39 cause The small diameter portion 2B of each of the sun gears 2m, 2o of the planetary gears Um, Uo of the planetary gears Um, Uo of the rear planetary gears adjacent to each other on the output side is fitted and fixed, whereby the planet carrier as described above. The sun gears 2m and 2o are fixed to the bodies 6i and 6m. As a result, the sun gears 2m, 2o are firmly and integrally fixed to the planet carrier bodies 6i, 6m of the adjacent input gears and intermediate planetary gears Ui, Um on the input side in a concentric manner. The tooth portion 2A is projected from 6m to the output side.

The sun gears 2m and 2o are pivotally supported by the support holes 8A and 8B via the bearings b5 and b6 by the through holes.

As a result, the planet carrier bodies 6i and 6m are
Is rotatably supported concentrically by the sun gears of the planetary gear stages U adjacent on the output side. The planet carrier body 6b of the planetary gear stage Uo of the output stage is concentrically held by fixing the carrier 4ob on the output side to the rear end of the output shaft 12.

Since the planet carrier bodies 6i, 6m, 6o are integrated, the carrier 4iA, 4m on the input side is formed.
A and 4oA can be set as free ends, but in this example,
As shown in FIG. 1, the carriers 4mA and 4oA are the output side carriers 4i of the input side planet carrier bodies 6i and 6m.
B and 4 mB are supported by the boss portion 39 formed through the bearing b7, and the input side carrier 4iA of the input stage planetary carrier body 6i is a protruding portion 41A of the bearing ring 41 provided on the input side bracket B1. Is supported by.

In this way, the sun gear 2 of the planetary gear stage U after the input stage is integrated with the planet carrier bodies of the adjacent planetary gear stages on the input side, and the sun gear 2 is connected to the input shaft 11,
By pivotally supporting the support shaft 8 projecting from the output shaft 12, the planet carrier bodies 6m, 6o of the planetary gear stage on the input side of the final planetary gear stage are coaxial with the input shaft 11 and the output shaft 12. It can be held.

As a result, in the planetary gear stage Ui, the planetary gear 5i of the carrier body 6i meshes with the sun gear 2i of the input shaft 11, which is the rotor shaft, and the internal gear 3i, whereby the rotational speed of the input shaft 11 is increased. The sun gear 2m of the intermediate planetary gear stage Um is rotated at the revolving speed of the planetary gear 5i that has been decelerated by a known reduction ratio that is determined according to the gear ratio, and the intermediate planetary gear stage Um is similarly decelerated. The sun gear 2o of the planetary gear stage Uo of the output stage is rotated.

As a result, the planet carrier 6o of the final planetary gear stage Uo further decelerates the rotation speed of the sun gear 2o according to the gear ratio, and rotates the output shaft 12 via the carrier 4oB.

As described above, in this embodiment, the planet carrier body is pivotally supported by the support shaft, so that the planet carrier body can rotate concentrically with the sun gear, and the support is uniform, and the structure is simplified. At the same time, the axial length can be reduced.

In the planetary gear device of the present invention,
In addition to the above-described embodiment, a so-called deceleration / acceleration device that does not use the electric motor M can be used, or a planetary gear device that uses a planetary gear with an arbitrary number of gears can be formed by using a leg instead of a flange type.

[0043]

As described above, the planetary gear device of the present invention is
Each planet carrier body is concentrically held by the support shaft protruding from the input shaft or the output shaft through the next-stage sun gear that is fixed, and as a result, the structure can be greatly simplified and the radial eccentricity is reduced and supported. Can be made uniform to improve the meshing accuracy between gears and reduce noise.

Further, by reducing the eccentricity, it is possible to improve the load distribution ratio in the planetary gears, reduce the vibration, and suppress the uneven wear to achieve the gear, the life of the device, and the downsizing.

[Brief description of drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

FIG. 2 is a front view thereof.

FIG. 3 is an exploded perspective view showing a main part thereof.

FIG. 4 is a front view illustrating a press punching plate.

FIG. 5 is a sectional view thereof.

FIG. 6 is a cross-sectional view illustrating a conventional device.

FIG. 7 is a cross-sectional view illustrating a conventional device.

[Explanation of symbols]

1 Planetary gear device 2, 2i, 2om, 2o Sun gear 3, 3i, 3m, 3o Internal gear 4, 4iA, 4iB, 4mA, 4mB, 4oA, 4oB
Carrier 5, 5i, 5m, 5o Planetary gear 6,6i, 6m, 6o Planet carrier body 7 Housing member 9 Press blank plate 10 Phase matching fitting part 11 Input shaft 12 Output shaft Ui, Um, Uo Planetary gear stage

Claims (2)

[Claims] 1. A planet comprising a sun gear, an internal gear that surrounds the sun gear, and a planet carrier body in which a planet gear that meshes with the sun gear and the internal gear is rotatably and integrally supported between a pair of carriers. A planetary gear device incorporating a plurality of gears in a housing member, wherein the input shaft is provided with a sun gear of the planetary gear on the input side, and each sun gear of the planetary gear after the output gear is connected to the sun gear. The planetary carrier bodies of the planetary gear stages adjacent to each other on the input side are integrated with each other, and the planetary carrier body of the most planetary gear stage is fixed to the output shaft. A planetary gear device, wherein the planetary gear device is rotatably supported by a support shaft concentrically provided on the output side end face of the output shaft or the input side end face of the output shaft. 2. The sun gear of the next planetary gear next adjacent to the planetary gear of the input side is output by the support shaft of the output side end surface of the input shaft and the sun gear of the planetary gear of the highest stage. 2. The planetary gear device according to claim 1, wherein the planetary gear device is rotatably supported by a support shaft on an input side end surface of the shaft.