JPH0874944A - Planetary gear device - Google Patents

Abstract

PURPOSE: To reduce a dimension in the axial direction, to increase productivity, and to lower costs by rotationally supporting an outer circumferential face of a carrier pivoting planet gears by means of a bearing ring, which is concentric with a sun gear arranged in a housing member and has an inner circumferential face made of lubricating material. CONSTITUTION: In a planetary gear device 1 serving as a flange type gear motor having an electric motor M, two stages of planet gear shifting units U (Ui, Uo) 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. An outer circumferential face 4b of the carrier 4 is rotationally supported by means of inner circumferential faces 13a of bearing rings 13A, 13B arranged in the annulus 3 in parallel. In other words, carriers 4iA, 4iB in the planet gear shifting unit Ui on the input side are supported on the inner circumferential faces of the bearing rings 13A, 13B made of lubricating material, while a carrier 4oA in the planet gear shifting unit Uo on the output side is supported on the inner circumferential face of the bearing ring 13B.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention rotatably supports the outer peripheral surface of a carrier that pivotally supports a planetary gear by means of a bearing ring arranged in a housing member, thereby reducing the axial dimension and improving productivity. The present invention relates to a planetary gear device that can reduce

[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. The first prerequisite is to do it.

Therefore, for example, Japanese Patent Laid-Open No. 5-24031
As shown in FIG. 8, the carrier A has an outer periphery supported by a ball bearing C arranged in a housing, as disclosed in FIG. 8, and as disclosed in JP-B-59-30938, as shown in FIG. As shown in, the planetary gear D
It is known that a planet ring E having the same diameter as the pitch circle is provided and the planet ring E is rolled by an outer shell 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 one shown in FIG. 8, 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. 9, 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.

An object of the present invention is to provide a planetary gear device which is inexpensive and can be downsized on the basis that the outer peripheral surface of the carrier is rotatably supported by a bearing ring made of a self-lubricating material.

[0009]

The present invention comprises a sun gear and
A planetary gear device in which a housing is provided with a planetary gear stage 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 on a carrier. The carrier has a circular outer peripheral surface and is arranged in the housing member adjacent to the inner gear and is concentric with the sun gear and has an inner peripheral surface made of a lubricating material. In the planetary gear device, the outer peripheral surface of the carrier is rotatably supported on the inner peripheral surface.

[0010]

Since the outer peripheral surface of the carrier is supported by the bearing ring made of a self-lubricating material, and the outer peripheral surface of the carrier is generally large in diameter, the bearing pressure can be made relatively small, and as a result, the bearing pressure can be reduced. Since it is possible to make the ring to have substantially the same width as the carrier, it is possible to suppress an increase in the axial size of the device and simplify the structure. In particular, the bearing ring is ring-shaped and can be formed into a simple shape, so that the bearing ring can be manufactured inexpensively and easily, for example, by molding.

Further, when the bearing ring is formed of synthetic resin, noise accompanying contact with the carrier can be reduced, and when a plurality of planetary gears are used, one carrier having adjacent planetary gears facing each other can be reduced. When supporting using a wide bearing ring, it is possible to maintain concentricity between adjacent gears.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. 1 to 6, the 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.
The outer peripheral surface 4b of the carrier 4 is rotatably supported by the inner peripheral surface 13a of the bearing ring 13 arranged side by side with the internal gear 3.

In this embodiment, the internal gear 3 uses a punching laminated body 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 embodiment, the planetary gear stage U has two planetary gear stages Ui and Uo on the input side and the output side (i and o are used as necessary when distinguishing the input side and the output side. The same applies hereinafter. ), The planetary gear stage Ui on the input side includes the sun gear 2i formed at the rotor shaft of the electric motor M, that is, the tip end of the input shaft 11 of the planetary gear device 1, and the sun gear 2i supported by the housing member 7. Surrounding internal gear 3i, coupling shaft 21, ..., Support shaft 2
2 are connected by two carriers 4iA, 4iB and a plurality of support shafts 22 and a planetary carrier body 6i in which a planetary gear 5i is pivotally supported, and the input side carrier 4iA is The inner peripheral surface 13a of the first bearing ring 13A and the output side carrier 4iB are rotatably supported by the inner peripheral surface 13a of the second bearing ring 13B. The sun gear 2i does not directly cut the input shaft 11,
As shown in FIG. 7, it may be a separate body.

Further, the planetary gear stage Uo on the output side has a sun gear 2o fixed to the center of the carrier 4iB, an internal gear 3o supported by the housing member 7 and surrounding the sun gear 2o, and two carriers 4oA, Similarly, a planetary carrier body 6o having a planetary gear 5o ...
The input side carrier 40A is composed of the second
The carrier 4oB on the output side is supported by the inner peripheral surface 13a of the bearing ring 13B, and is fixed to the rear end of the output shaft 12.

The housing member 7 is made up of the electric motor M.
A cylindrical motor housing Hm having a bottom and surrounding the stator extends beyond the stator, an input-side bracket B1 inserted into the insertion portion 24, and a front end of the insertion portion 24. And an output side bracket B2 that is fitted into the. Between the input and output side brackets B1 and B2, the first bearing ring 13A, the internal gear 3i, the second bearing ring 13B, and the internal gear 3o are arranged side by side from the input side. To be done.

Further, the insertion portion 24 is capable of accommodating the planetary gear stage U and has a diameter slightly larger than that of the portion accommodating the stator, so that the bracket B on the input side is formed.
It has a step 25 for positioning 1. The input shaft 11, that is, the sun gear 2i is formed by the bearing b1 of the bracket B1 on the input side and the bearing b2 on the rear wall of the motor housing Hm.
Are supported concentrically with the insertion portion 24. As shown in FIG. 2, the bracket B2 on the output side is provided with a flange 27 having mounting holes at four corners, an outer cylinder portion 28 fitted and fixed to the insertion portion 24, and a core coaxial with the insertion portion 24, Accordingly, the output shaft 12 is concentric with the input shaft 11 and its sun gear 2i, and the bearings b3, b
4 and an inner cylinder portion 29 supported by 4. The input shaft 11 and the output shaft 12 are sealed by seals S1 and S2.

The motor housing Hm has a length for forming the electric motor M, and may be separably connectable with a housing member for accommodating the planetary speed stage U.

In the present embodiment, the internal gears 3i, 3o are formed by punching and stacking the press punched plate 9 as described above. The press punched plate 9 is formed by punching a metal plate by fine blanking. To be done. As shown in FIGS. 5 and 6, in this example, the press punched plate 9 has an inner peripheral surface 9a having an inner tooth portion 3A and serving as a tip circle of the inner tooth portion 3 and a concave groove 31 for confirming the alignment position. A phase-matching fitting portion 10 is formed in a ring shape by punching a core outer peripheral surface 9b, and includes a concave portion 10A provided on one surface and a convex portion 10B which can be fitted in the concave portion 10A and provided on the other surface. Is forming.

As is well known, the fine blanking process was 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 has been confirmed that about 0.7 module is possible when the plate thickness is about 2.5 mm. Further, after punching, it is possible to carry out strain relief processing, or it is also possible to carry out hardening treatment of appropriate surfaces such as liquid immersion, nitriding, tufftride, and teeth, and at that time, the treatment should be carried out at the lowest temperature and in the shortest possible time. It is better that it does not generate distortion.

As described above, when the punching laminated body precision punched by the fine blanking process 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.

Further, since the internal gear 3 has a ring shape made of a punched laminated body of the press punched plates 9 ..., The rigidity in the radial direction is reduced as compared with the case of an integrated product having the same thickness, and the radial direction is increased. It also increases the flexibility of the tooth and helps improve tooth contact.

Further, the phase matching fitting portion 10 of the press punching 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, the concave and convex portions 10A and 10B on the front and back sides are slightly angled in the circumferential direction on the front and back sides so that they are within the range of the backlash of the meshing of the internal gear 3 and the planetary gear 5 over the entire width of the internal gear. It can also be offset. As a result, due to the stacking, the tooth lines are tilted within the range of the backlash and the phases of the inner tooth portions 3A are aligned, so that the gear transmission can be transmitted without play.

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, the convex portion 10B and the concave portion 10A are different in phase from the internal tooth portion 3A.
The fitting is always performed only at a fixed position, facilitating manual work or mechanical automatic assembly and eliminating fitting error.
Further, by providing the press punched plates 9 concentrically with each other, the press punched plates 9 are concentrically overlapped with each other by providing the positions at three or more positions which are deviated from each other about the trisecting position.

Further, as shown in an enlarged view in FIG. 4, a concave portion 10A on the input side surface of the press-extracting plate 9 on the most input side of the internal gear 3i is a convex portion provided on the output side surface of the first bearing ring 13A. Fit to part 10C. The first bearing ring 1
Similarly, a concave portion 10D is also provided on the input side surface of 3A, and the concave portion 10D is fitted to the convex portion 10E of the adjacent input side bracket B1.
Further, the convex portion 10B on the output side surface of the press-extracting plate 9 on the most output side of the internal gear 3i fits into the concave portion 10F on the input side adjacent surface of the second bracket B2. Further, the concave portion 10A on the surface on the most input side of the internal gear 3o is fitted with the convex portion 10G on the surface adjacent to the output side of the second bearing ring 13B. The convex portion 10B on the most output side of the internal gear 3o is fitted into the concave portion 10H of the output side bracket B2.

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

The recesses and protrusions may be reversed from those shown in the figure, and as long as they can be fitted on the adjacent surfaces, for example, the recesses 10D and the protrusions 10E of the first bearing ring 13A and the bracket B1 on the input side, etc. It is also possible to change the positions in the circumferential direction and the radial direction from those of the concave and convex portions. Further, the convex portion and the concave portion can adopt various shapes such as a so-called circular shape and a non-circular shape such as a quadrangle. The bearing rings 13A and 13B, the brackets B1 and B2, and the like may all be formed with recesses, and they may be joined by the alignment pins shown in FIG.

Further, in the present embodiment, 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 for aligning the phase and, for example, a V-shaped metal object (not shown). ) Can be used for the integration of the punched laminated body such as by inserting in the longitudinal direction.

Further, the outer peripheral surface 9b of each press-punched plate 9 and the outer peripheral surface 13 of the first and second bearing rings 13A and 13B.
In the present embodiment, the diameter d of b is slightly smaller than the inner diameter D of the inner peripheral surface 24a of the insertion portion 24 of the motor housing Hm as shown in FIG. A radial gap G is created between the surfaces on which the brackets B1 and B2 on the output side and the output side face each other.

On the other hand, both side edges of the outer peripheral surface 9b of each press punched plate 9 and the outer peripheral surfaces 13b of the bearing rings 13A and 13B.
Continuous chamfered portions 15 are provided on both side edges of the press punched plate 9, and thus two chamfered portions 15 and 15 are provided on the outer circumference between the press punched plate 9 and the bearing rings 13A and 13B which are adjacent to each other by stacking. A combined U-shaped or V-shaped mounting groove 16 is formed. In this mounting groove 16, vibration-proof materials 17 made of, for example, rubber (oil resistant rubber), which are O-rings in this example, are arranged.

In addition to the circular cross section, the vibration-proof material 17 may have various non-circular shapes such as a triangular shape and a star shape, or a tubular shape. Further, the vibration-proof material 17 may be preliminarily adhered to the mounting groove 16, and at that time, it may be made into one to several cord-like bodies without being preliminarily formed into an annular shape. Further, the mounting groove 1
The depth of 6 is greater than 1/2 of the radial height of rubber, 2 /
It is preferable that the insertion depth is relatively large, such as about 3 or less, to prevent the detachment when attaching to the housing member 7.
In addition, the press punched plate 9, the outer peripheral surfaces 9b of the bearing ring 13, 1
A rubber coating layer may be baked and formed on 3b, or a rubber sheet may be arranged.

Further, the press punching plate 9 and the bearing ring 13 are supported by the insertion portion 24 with the vibration isolator 17 abutting against the inner peripheral surface 24a of the insertion portion 24 of the housing member 7. As a result, the internal gear 3 which is a punched laminated body of the press punched plate 9 is provided with a cushioning function in the circumferential direction and the radial direction,
This helps to mitigate the impact when meshing with the planetary gears 5. Further, the shock and vibration itself which have been eased are absorbed and mitigated by the vibration isolator 17 and their transmission to the motor housing Hm is suppressed, so that the vibration and sound are prevented from diverging to the outside, and the noise of the device is reduced, Low vibration is possible. Bearing ring 1
The vibration damping material 17 of No. 3 suppresses the vibration caused by the sliding contact with the carrier 4.

Further, the first and second bearing rings 13A, 1
3B has a ring shape having a concentric inner peripheral surface 13a and an outer peripheral surface 13b.
When the outer peripheral surface 13b is inserted into the insertion portion 24 of the motor housing Hm that is concentric with the vibration isolator 17, the inner peripheral surface 13a is concentric with the input shaft 11.

The first and second bearing rings 13A, 13
B is a synthetic resin having a self-lubricating property such as a hard resin containing a lubricant such as a fluororesin or molybdenum sulfide as a whole,
As shown in FIG. 4, a thin annular support piece 13m, which is made of self-lubricating metal such as oil-impregnated metal, is retained by an annular base 13n and protrusion-shaped locking portions 13P1 and 13P2 arranged on the inner peripheral side thereof. The inner peripheral surface 13a is formed by using the self-lubricating material.

The inner peripheral surface 13a has the inner gear 3i,
The first bearing ring 13A has the same width as the carrier 4iA on the input side of the planet carrier body 6i and supports it, and the second bearing ring 13B is , The carrier 4iB on the output side of the planet carrier body 6i and the carrier 4o on the input side of the planet carrier body 6o.
By supporting both A and the input shaft 11 concentrically,
The concentricity of the planet carrier bodies 6i and 6o is improved. Therefore, the second bearing ring 13B is the same as the first bearing ring 1B.
The width in the axial direction is about twice as large as that of 3A. The carrier 4oB on the output side of the planet carrier body 6o is fixed to the rear end of the output shaft 12 as described above, so that it becomes concentric with the insertion portion 24, that is, the input shaft 11.

The first and second bearing rings 13A, 13
The carrier 4iA and the carrier 4i rotatably supported by B
The outer peripheral surface 4b of the carrier B and the carrier 4oA has a circular shape with a diameter capable of abutting the inner peripheral surface 13a of each of the supported bearing rings 13A and 13B, and the outer peripheral surface 4b of the carrier and the bearing rings 13A and 13B. The radial gap g from the inner peripheral surface 13a is determined according to the intersection of the center distances of the gear precision to be adopted.

Further, the carrier 4i of the planet carrier body 6i
A, 4iB, and carrier 4o of the planet carrier body 6o
A and 4oB are both the plurality of coupling shafts 2 with steps at both ends.
1 and a plurality of support shafts 22 having the same shape as the coupling shaft 21 are integrally coupled to each other, and the support shaft 22 has a cylindrical bearing 35 and thrust bearings 36, 36 (only shown in FIG. 1). With the planetary gears 5i, 5
O is rotatably supported to form the planet carrier bodies 6i and 6o. In the planet carrier body 6i, the carrier 4iA and the carrier 4iB are the bearing ring 13
The input shaft 11 is held concentrically by being guided by the inner peripheral surfaces 13a of A and 13B.

The output side carrier 4iB of the planet carrier body 6i has a boss portion 39 projecting toward the output side at the center thereof, and the center hole of the boss portion 39 allows the output side planetary speed change stage to be formed. The small diameter portion 2oA at the rear end of the Uo sun gear 2o is fitted and fixed, whereby the sun gear 2o is
It is concentric with the sun gear 2i. Note that various well-known methods such as a key, notch, knurling, press-fitting, and bonding can be used for fixing.

In this 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 input shaft 1
The sun gear 2o of the planetary gear stage Uo is rotated at the revolution speed of the planetary gear 5i, which is obtained by reducing the number of revolutions of 1 at a known reduction ratio determined according to the gear ratio.

Similarly, in the planet carrier 6o, the carrier 4oA on the input side has an inner peripheral surface 13a of the bearing ring 13B.
The carrier 4oB on the output side is fixed at the rear end of the output shaft 12 so that it is held concentrically with the input shaft 11 and rotates.

As a result, in the planet carrier 6o, the planet gear 5o meshes with the sun gear 2o and the internal gear 3o, so that the rotation speed of the sun gear 2o rotating at the above rotation speed can be adjusted according to the gear ratio. The output shaft 12 is rotated via the carrier 4oB at the revolution speed of the planetary gear 5o that has been further reduced by a known reduction ratio determined by the above.

Thus, in this example, the carriers 4i, 4
Since the iB and 4oA are pivotally supported by the bearing rings 13A and 13B, the planet carrier body 6 can be rotated concentrically with the sun gear 2 and the support can be made uniform, and at the same time, the structure can be simplified and the The length can be reduced.

In FIG. 7, the internal gears 3i and 3o are integrally formed, and the recesses and protrusions of the phase-matching fitting portion 10 are not adopted. Further, the internal gears 3i and 3o are directly attached to the housing member 7 without interposing the vibration isolator 17. 7 shows another embodiment of the present invention that is made.
Also, in this example, the carrier 4 on the output side of the planet carrier 6b is
The oB is also rotatably supported by the third bearing ring 13C. At this time, the output shaft 12 can be joined with play only by a rotation stopper that prevents relative rotation.

In the planetary gear device of the present invention,
In addition to the above-described embodiment, a so-called deceleration / accelerator device which does not use the electric motor M is used, and a flange type is used instead of a leg type.
Alternatively, more than two planetary gears can be used.

[0047]

As described above, the planetary gear device of the present invention is
Since the carrier is rotatably supported by the bearing ring whose inner circumferential surface is made of self-lubricating material, the structure of the device is simplified, and it is useful for downsizing and cost reduction, such as reducing the axial dimension, especially as a device with a small capacity. It can be suitably formed.

[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 cross-sectional view illustrating an assembled state of an internal gear, a bearing ring, and an elastic body.

FIG. 5 is a front view illustrating a press punching plate.

FIG. 6 is a sectional view thereof.

FIG. 7 is a sectional view showing another embodiment.

FIG. 8 is a cross-sectional view illustrating a conventional device.

FIG. 9 is a cross-sectional view illustrating a conventional device.

[Explanation of symbols]

 1 planetary gear device 2, 2i, 2o sun gear 3, 3i, 3o internal gear 4, 4iA, 4iB, 4oA, 4oB carrier 4b outer peripheral surface 5, 5i, 5o planetary gear 6, 6i, 6o planetary carrier body 7 housing member 9 Press punching plate 10 Phase matching fitting part 11 Input shaft 12 Output shaft 13, 13A, 13B Bearing ring 13a Inner peripheral surface Ui, Uo Planetary gear stage

Claims (1)

[Claims] 1. A planetary gear stage comprising a sun gear, an internal gear surrounding the sun gear, and a planet carrier body in which a carrier rotatably and integrally supports a planet gear that meshes with the sun gear and the internal gear. A planetary gear device assembled in a housing member, wherein the carrier has a circular outer peripheral surface, is arranged on the housing member adjacent to the inner gear, is concentric with the sun gear, and is made of a lubricating material. A planetary gear device characterized in that the outer peripheral surface of the carrier is rotatably supported by the inner peripheral surface of an annular bearing ring having a surface.