JPH08170695A - Rotary supporting device for planet gear - Google Patents

Abstract

PURPOSE: To provide a structure applying a uniform load to each planet gear and a supporting shaft for supporting each of these planet gears regardless of dimensional error and assembly error of a constitutional part. CONSTITUTION: Partly planet gears 3A, 3A are supported to the first planet gear carrier 27. The rest of planet gears 3B, 3B are supported to the second planet gear carrier 28. The fellow these first/second planet gear carriers 27, 28 are combined elastically displaceably over a circumferential direction. In the case of applying a large load partly to the planet gear 3A, the fellow first/ second planet gear carriers 27, 28 are elastically displaced over a circumferential direction, to support the load also to the rest of the planet gear 3B.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The planetary gear rotation support device according to the present invention rotatably supports a planetary gear incorporated in a planetary gear device which constitutes an automatic transmission for automobiles or a transaxle around a support shaft. To use for.

[0002]

2. Description of the Related Art Conventionally, as a planetary gear rotation supporting device for a planetary gear device that constitutes an automatic transmission for an automobile, FIG.
The structures shown in 0 to 32 are widely known. This conventionally known rotation supporting device for a planetary gear has a tooth 1 on the outer peripheral surface.
A plurality of (generally 3 to 4) planetary gears are provided between the sun gear 1 having a formed therein and the ring gear 2 arranged concentrically with the sun gear 1 and having teeth 2a formed on the inner peripheral surface thereof. 3 are arranged at equal intervals in the circumferential direction. Then, the teeth 3a formed on the outer peripheral surfaces of the plurality of planetary gears 3 are replaced by the teeth 1
a and the tooth 2a.

The plurality of planetary gears 3 are rotatably supported around a support shaft 4 via a plurality of rollers 12, 12, respectively. A base end portion (left end portion in FIGS. 30 to 31) of the support shaft 4 is supported and fixed to a support plate 5 which is rotatable around the sun gear 1. In the illustrated example, the sun gear 1 is formed into a cylindrical shape, and the support plate 5 is formed into an annular shape with an L-shaped cross section. The cylindrical portion 6 formed on the inner peripheral edge of the support plate 5 is spline-engaged with the outer peripheral surface of the rotary shaft 7. The sun gear 1
Is supported around the rotary shaft 7 so as to be rotatable relative to the rotary shaft 7. Further, the ring gear 2 is supported around these respective members so as to be rotatable relative to the respective members.

Further, the tips of the plurality of support shafts 4 (see FIGS. 30 to 3)
The right end portion 1) is internally fitted and fixed in a circular hole 9 formed in a locking plate 8 formed in a circular ring shape, and the tip portions of the plurality of support shafts 4 are connected to each other. On the outer peripheral surface of the intermediate portion of the plurality of support shafts 4, a portion between the support plate 5 and the locking plate 8 is a cylindrical inner ring raceway 10. On the other hand, the inner peripheral surface of the planetary gear 3 is a cylindrical outer ring raceway 11. A plurality of rollers 12, 12 are provided between the inner ring raceway 10 and the outer ring raceway 11 so that the planetary gear 3 is located between the locking plate 8 and the support plate 5 around the intermediate portion of the support shaft 4. To
It is rotatably supported. It should be noted that an oil passage hole 13 is provided inside the support plate 5 and each support shaft 4 so that the plurality of rollers 1
Lubricating oil can be sent freely to the installation locations of 2 and 12.

In the planetary gear rotation support device constructed as described above, the rotary shaft 7 is used as a drive shaft or a driven shaft, and the center of the sun gear 1 or the ring gear 2 is coupled to the driven shaft or the drive shaft. And, which gears 1, 2, 3 are rotatable,
By changing which of the gears 1, 2, and 3 is made non-rotatable, gear shifting between the drive shaft and the driven shaft and conversion of the rotation direction are performed. Since the structure and operation of such a planetary gear device itself are well known in the art, the illustration and detailed description of the entire structure will be omitted.

[0006]

By the way, in the case of the planetary gear rotation support device as described above, an excessive load may be applied to some members due to dimensional errors and assembly errors of the constituent members. There is. That is, the support shafts 4 that rotatably support the planetary gears 3 are arranged at equal intervals in the circumferential direction, and the planetary gears 3 having the same pitch circular dimension are rotatably arranged around each support shaft 4. To support. If these relationships are strictly adhered to, no particular problems will occur. That is, if the planetary gears 3 having completely the same size are rotatably supported around the support shafts 4 which are completely evenly arranged, through the rollers 12, 12 having completely the same outer diameter, A uniform load is applied to each planetary gear 3 and the support shaft 4. Therefore, the durability of some of the planetary gears 3 and the like is not impaired.

However, when the dimensions of the above-mentioned parts deviate from the predetermined values due to unavoidable manufacturing errors and assembly errors, the load applied due to the power transmission between the sun gear 1 and the ring gear 2 is A part of the planetary gears 3 and the support shaft 4 and the rollers 12, 12 corresponding to the planetary gears are supported. In such a case, these planetary gears 3, support shafts 4,
A large load exceeding the design value is applied to the rollers 12, 12.
That is, when the planetary gear device is in operation, a radial load based on the revolution movement is applied to the planetary gear 3. When a particularly large amount of power is transmitted to a part of the planetary gears 3 due to the manufacturing error or the assembly error as described above, the radial load generated in the part of the planetary gears becomes extremely large. As a result, the outer ring raceway 1 formed on the inner peripheral surface of the planetary gear 3
1, the inner ring raceway 10 formed on the outer peripheral surface of the support shaft 4 and the rolling surfaces of the rollers 12, 12 are damaged early such as flaking, which impairs the durability of the planetary gear device.

In order to prevent such deterioration of durability due to dimensional error of each part, it has been conventionally practiced, for example, to use an actual flat blade 5-452.
The structure described in Japanese Patent Publication No. 97 is known. In the case of this conventional structure, as shown in FIG. 33, a minute annular gap 15 is formed between the outer peripheral surface of the support shaft 4 and the outer peripheral surface of the inner race 14, and the oil film layer is formed in the annular gap 15. 16 are provided. The above-mentioned dimensional error is absorbed by the annular gap 15 to prevent an excessive load from being applied to some members. However, in order to support a sufficient load by the oil film layer 16, the thickness dimension of the oil film layer 16 must be considerably reduced. In particular, in the case of a planetary gear device used in a transmission for automobiles, a considerably large load is applied, so that it is necessary to make the thickness dimension of the oil film layer 16 smaller. It becomes extremely small. Therefore, the structure described in the above publication is not practical.

Other than the above, the rotation supporting device for a planetary gear invented for a similar purpose includes, in addition to these, JP-A-60-3342, JP-A-61-188052, and JP-A-61-1868.
No. 52, No. 5-45296, No. 5-59.
Those described in Japanese Patent No. 107, etc. are known. However, the structures described in these publications are unsuitable for the structure of a planetary gear device for a transmission of an automobile, which requires transmission of a large amount of power, such as the assumption that the supporting shaft is supported by a cantilever. is there. The rotation support device for a planetary gear of the present invention is
This is intended to eliminate the above-mentioned inconvenience.

[0010]

All of the planetary gear rotation supporting devices of the present invention have the same center of rotation and are arranged parallel to each other, like the conventional planetary gear rotation supporting devices described above. A support plate and a locking plate, each of which is arranged in parallel with the center of rotation and on the same arc centered on the center of rotation, and has both ends supported by the support plate and the locking plate. A book support shaft and a plurality of planetary gears rotatably supported around an intermediate portion of each support shaft are provided.

Particularly, in the planetary gear rotation supporting device of the present invention, in the planetary gear rotation supporting device according to claim 1, the support plates are displaceable in a circumferential direction relative to each other. It consists of a combined first support plate element and second support plate element. Further, the locking plate is composed of a first locking plate element and a second locking plate element which are movably combined with each other in the circumferential direction. And both ends of a part of the support shafts of the plurality of support shafts are supported by the first support plate element and the first locking plate element, and among the plurality of planetary gears. It constitutes a first planetary gear carrier that supports a part of the planetary gears so as to freely rotate and revolve. Further, both end portions of the remaining support shafts of the plurality of support shafts are supported by the second support plate element and the second locking plate element, and the rest of the plurality of planetary gears are supported. The second planetary gear carrier that supports the planetary gears of FIG. Further, an elastic displacement portion is provided between the first planetary gear carrier and the second planetary gear carrier, which serves as a resistance against relative displacement between the two planetary gear carriers in the circumferential direction. There is.

Further, in the planetary gear rotation support device according to the present invention, both ends of a part of the plurality of support shafts cannot be displaced by the support plate and the locking plate. Supported by. Both ends of the remaining support shafts of the plurality of support shafts are supported by the support plate and the locking plate so as to be elastically displaceable in the circumferential direction.

[0013]

In any of the planetary gear rotation support devices of the present invention configured as described above, some of the plurality of support shafts and the remaining support shafts are arranged in the circumferential direction. It is elastically movable relative to each other. When a large load is applied to a part corresponding to a part of the support shaft due to a manufacturing error or an assembly error, the distance between the part of the support shaft and the remaining support shaft in the circumferential direction is elastic. Will be displaced. Therefore, not only the above-mentioned part of the support shafts but also the remaining support shafts bear the load applied from the ring gear or the sun gear to the planet gears. As a result, a large load is not applied to only part of the support shafts, and the durability of the entire planetary gear device can be improved.

[0014]

1 to 6 show a first embodiment of the present invention corresponding to claim 1. The feature of the present invention is that the spacing dimensions of the support shafts 4a and 4b adjacent to each other in the circumferential direction are not exactly equal, or the pitch circles of the planetary gears 3A and 3B supported by the support shafts 4a and 4b are not equal. Even if the diameters are not exactly equal, the structure prevents the excessive load from being applied to some members. Since the structure and operation of the other parts are the same as those of the conventional structure described above, redundant description will be omitted or simplified, and the characteristic part of the present invention will be mainly described below.

The support plate 5a and the locking plate 8a, each of which is formed in a circular ring shape, have a center of rotation (virtual center) that is coincident with each other.
And are arranged parallel to each other. Of these, the support plate 5a overlaps the first support plate element 17 and the second support plate element 18 in the axial direction (front and back directions in FIGS. 1 and 3, left and right directions in FIG. 2, and up and down directions in FIG. 4). Composed together. A cylindrical portion 6 is provided on the inner peripheral edge of the first support plate element 17 among these, and a female spline groove 19 is formed on the inner peripheral surface of the cylindrical portion 6. The female spline groove 19 engages with the male spline groove formed on the outer peripheral surface of the intermediate portion of the rotary shaft 7 (FIG. 30).
Further, circular holes 21, 21 are formed at two positions on the diametrically opposite sides, respectively, in a part of the circular ring portion 20 constituting the first support plate element 17.

On the other hand, a cylindrical portion 2 is provided at each of two positions on the diametrically opposite sides of a part of the second support plate element 18.
2, 22 are formed in alignment with the circular holes 21, 21. The outer diameter dimension of each of the cylindrical portions 22, 22 is smaller than the inner diameter dimension of each of the circular holes 21, 21. Therefore, in the state where the cylindrical portions 22, 22 are inserted into the circular holes 21, 21 in order to combine the first supporting plate element 17 and the second supporting plate element 18, the cylindrical portions 2 are inserted in the circular holes 21, 21.
An annular gap exists between the outer peripheral surface of 2, 22 and the inner peripheral surface of each circular hole 21, 21. The first and second support plate elements 17 and 18 are combined so as to be displaceable in the circumferential direction by the size of the gap.

The locking plate 8a is formed by stacking the first locking plate element 23 and the second locking plate element 24 in the axial direction. A part of the first locking plate element 23 among these is provided with circular holes 25, 25 at two positions on the diametrically opposite side, respectively.
Is formed. On the other hand, cylindrical portions 26, 26 are formed at the two positions on the diametrically opposite sides of the second locking plate element 24 so as to be aligned with the circular holes 25, 25, respectively. The outer diameter of each of the cylindrical portions 26, 26 has a circular hole 2
It is smaller than the inner diameter dimension of 5, 25. Therefore, in order to combine the first locking plate element 23 and the second locking plate element 24, the cylindrical portions 26, 26 are connected to the circular holes 25, 2 respectively.
In the state of being inserted into the cylindrical member 5, there is an annular gap between the outer peripheral surface of each of the cylindrical portions 26, 26 and the inner peripheral surface of each of the circular holes 25, 25. The first and second locking plate elements 23 and 24 are combined so as to be displaceable in the circumferential direction by the size of this gap.

Of the four support shafts 4a and 4b arranged at equal intervals in the circumferential direction, the two support shafts 2 located diametrically opposite to each other.
Both ends of the book support shafts 4a, 4a are supported by the first support plate element 17 and the first locking plate element 23.
Then, the first support plate element 17 and the first locking plate element 23, and the two support shafts 4a and 4a hung between the two elements 17 and 23, Of the planetary gear carrier 27. The first planetary gear carrier 27 is located diametrically opposite to the other four planetary gears 3A and 3B arranged at equal intervals in the circumferential direction.
The planetary gears 3A and 3A are supported so as to freely rotate and revolve.

Of the above four support shafts 4a and 4b,
The remaining two support shafts 4b, which are also positioned diametrically opposite to each other,
Both ends of 4b are supported and fixed to a cylindrical portion 22 formed on the second support plate element 18 and a cylindrical portion 26 formed on the second locking plate element 24. The second support plate element 18 and the second locking plate element 24, and the two support shafts 4b and 4b that are bridged between the two elements 18 and 24, Of the planetary gear carrier 28. The second planetary gear carrier 28 is composed of four planetary gears 3A and 3B arranged at equal intervals in the circumferential direction, and the remaining two planetary gears 3B located diametrically opposite to each other.
3B is supported to rotate and revolve freely.

Further, between the first planetary gear carrier 27 and the second planetary gear carrier 28, there is resistance against relative displacement between the two planetary gear carriers 27, 28 in the circumferential direction. The elastic displacement portion is provided. To this end, the first and second support plate elements 17, 18
The connecting pins 29, 29 are provided at four locations in the circumferential direction on the first and second locking plate elements 23, 24, respectively. In order to bridge these connecting pins 29, 29, the portions of the first and second support plate elements 17, 18 aligned with each other at four positions in the circumferential direction are circled as shown in FIG. The holes 30a and 30b are formed. In addition, the first,
As shown in FIG. 4, circular holes 31a and 31b are formed in the portions of the second locking plate elements 23 and 24 that are aligned with each other at four circumferential positions. The connecting pins 29, 29 have the circular holes 30a, 30b, 31a,
By inserting 31b without rattling and crushing the tip end into a rivet shape, the first and second support plate elements 17 and 18 and the first and second locking plate elements 23 and 24 are connected. ing.

Furthermore, the circular holes 30a and 31a are formed in a part of the first support plate element 17 and the first locking plate element 23.
At positions sandwiching from both sides in the circumferential direction, rectangular through holes 32, which are long in the diametrical direction of the support plate elements 17 and 18, respectively.
32 are formed. Then, these through holes 32, 32
The portions between the circular holes 30a and 31a are narrow portions 33 and 33 that are elastically deformable. Each of these narrow parts 3
3, 33 form an elastic displacement portion that serves as a resistance against relative displacement of the two planetary gear carriers 27, 28 relative to each other in the circumferential direction.

The planetary gear rotation support device of the present invention constructed as described above is formed at equal intervals in the circumferential direction.
Of the two support shafts 4a and 4b, the two support shafts 4a and 4a located diametrically opposite to each other and the remaining two support shafts 4b and 4b
and b are elastically displaceable relative to each other in the circumferential direction. That is, a first planetary gear carrier 27 configured to include the two support shafts 4a and 4a, and a second planetary gear carrier 28 configured to include the remaining two support shafts 4b and 4b. When a strong force is applied in the circumferential direction between
The elastic displacement of the narrow portions 33, 33 allows the planetary gear carriers 27, 28 to be relatively displaced in the circumferential direction.

Therefore, when a large load is applied to the planetary gear 3A (or 3B) supported by a part of the support shafts 4a (or 4b) due to a manufacturing error, an assembly error, or the like, this part of the support shafts 4a (or 4b) and the remaining support shaft 4b (or 4
The circumferential distance from a) changes elastically. Therefore, not only the part of the support shaft 4a (or 4b) but also the remaining support shaft 4b (or 4a) bears the load applied from the ring gear 2 or the sun gear 1 to the planet gears 3A, 3B.
As a result, a large load is not applied to only part of the support shafts 4a (or 4b), and the durability of the entire planetary gear device can be improved.

For example, the two planetary gears 3A, 3A
In addition, when a larger load than the remaining two planetary gears 3B and 3B is applied in the clockwise direction in FIG. 1, the first support plate that supports both ends of the two support shafts 4a and 4a. Element 1
7 and the first locking plate element 23, as shown by arrows in FIG. 6 (A), the second support plate element 18 and the second locking plate element 24.
On the other hand, it tends to be displaced to the right in the figure. As a result, as shown in FIG. 6 (B), the narrow portion 33 existing on the rear side in the displacement direction (left side in FIG. 6) is pushed by the connecting pin 29 and elastically deformed, and the first planetary gear carrier 27. And the second planetary gear carrier 28 are slightly displaced in the circumferential direction. This displacement is performed in a direction in which the loads applied to the planetary gears 3A and 3B are equalized. Therefore, even if there are manufacturing errors and assembly errors as described above, at least two planetary gears 3A and 3B are applied with a substantially uniform load. And
As described above, the durability of the entire planetary gear device can be improved.

Next, FIG. 7 shows a second embodiment of the present invention corresponding to claim 1. In the case of the present embodiment, through holes 32, 32 are formed on both sides in the circumferential direction of the circular hole 30b formed in the second support plate element 18 and the circular hole 31b formed in the second locking plate element 24, respectively. Is formed. Therefore,
When the first and second planetary gear carriers 27, 28 are displaced relative to each other in the circumferential direction, the second support plate element 1
8 and the narrow portions 33, 3 formed on the second locking plate element 24.
3 is elastically deformed. Other configurations and operations are similar to those of the above-described first embodiment.

Next, FIGS. 8 to 9 correspond to claim 1.
The 3rd-4th Example of this invention is shown. In the first embodiment described above, the through holes 32 for forming the narrow portions 33, 33,
While the shape of 32 is a long rectangle, in the third embodiment shown in FIG. 8, these through holes 32, 32 are circular,
The fourth embodiment shown in FIG. 9 has an elliptical shape. Other configurations and operations are similar to those of the first embodiment described above.

Next, FIG. 10 shows a fifth embodiment of the present invention corresponding to claim 1. In the case of this embodiment,
The inner diameters of the circular holes 30a and 31a formed in the first support plate element 17 and the first locking plate element 23 for inserting the connecting pin 29 are sufficiently larger than the outer diameter dimension of the connecting pin 29. are doing. And these circular holes 30a, 31a
Between the inner peripheral surface of the and the outer peripheral surface of the connecting pin 29, rubber,
Elastic materials 34, 34 such as an elastomer and a synthetic resin are sandwiched in an elastically compressed state. In the case of the present embodiment, each of these elastic members 34, 34 constitutes an elastic displacement portion that serves as a resistance against relative displacement of the first and second planetary gear carriers 27, 28 relative to each other in the circumferential direction. The configuration and operation are the same as those in the above-described first embodiment except that the elastic displacement portions are replaced with the elastic members 34, 34 from the narrow portions 33, 33.

Next, FIG. 11 shows a sixth embodiment of the present invention corresponding to claim 1. In the case of this embodiment,
The inner diameters of the circular hole 30b formed in the second support plate element 18 and the circular hole 31b formed in the second locking plate element 24 are
The outer diameter of the connecting pin 29 is made larger. The elastic members 34, 34 are sandwiched between the inner peripheral surfaces of the circular holes 30b, 31b and the outer peripheral surface of the connecting pin 29. Therefore, the first and second planetary gear carriers 27, 2
When the eight members are relatively displaced in the circumferential direction, the elastic members 34, 34 provided on the second support plate element 18 and the second locking plate element 24 are elastically deformed. Other configurations and operations are similar to those of the fifth embodiment described above.

Next, FIGS. 12 to 15 show a seventh embodiment of the present invention, which corresponds to the first aspect. In the case of the present embodiment, by connecting the first planetary gear carrier 27 and the second planetary gear carrier 28 with a plurality of elastic connection pieces 35, 35, both planetary gear carriers 27, 28 are connected.
It is elastically displaceable in the circumferential direction. In the case of the present embodiment, each of the elastic connecting pieces 35, 35 constitutes an elastic displacement portion that serves as a resistance against relative displacement of the first and second planetary gear carriers 27, 28 relative to each other in the circumferential direction. To do.

In order to provide such elastic coupling pieces 35, 35, the first supporting plate element 17 and the first locking plate element 23 constituting the first planetary gear carrier 27 are provided with a first The connecting pins 36 of 36 are bridged. Further, between the second support plate element 18 and the second locking plate element 24 which form the second planetary gear carrier 28, a second connecting pin 37,
I am crossing over 37. The first supporting plate element 17
And a part of the first locking plate element 23, the through holes 3 are formed in the portions where the second connecting pins 37, 37 penetrate.
8 and 38 are formed. The inner diameters of the through holes 38, 38 are larger than the outer diameters of the second connecting pins 37, 37, and the second connecting pins 37, 37 are located inside the through holes 38, 38. , Loosely inserted. Therefore, the relative displacement of the first and second planetary gear carriers 27, 28 in the circumferential direction is the same as the inner peripheral surface of the through holes 38, 38 of the outer peripheral surfaces of the second connecting pins 37, 37. Only the gap that exists between is allowed.

The elastic connecting pieces 35, 35 are integrally formed of an elastic material such as metal or synthetic resin, and have locking holes 39, 39 at both ends thereof. The intermediate portions of the first and second connecting pins 36 and 37 are inserted into the locking holes 39 and 39, respectively. Further, an elastically deforming portion 40 is formed at an intermediate portion between the elastic connecting pieces 35, 35. The elastically deforming portion 40 is provided in an offset state with respect to a straight line connecting the centers of the locking holes 39, 39 at both ends. This elastic deformation portion 40 is shown in FIG.
4A has a shape as shown in FIG. 4A, but when a load in the compression direction is applied, it is shown in FIG. 4B, and when a load in the tension direction is applied, it is shown in FIG. 4C. Similarly, each elastically deforms. Other configurations and operations of this embodiment in which the first and second planetary gear carriers 27, 28 are connected by the elastic connecting pieces 35, 35 as described above are the same as those in the first embodiment described above.

Next, FIGS. 16 to 19 show an eighth embodiment of the present invention, which corresponds to the second aspect. In the case of the present embodiment, a plurality of (for example, three or four) arranged at equal intervals in the circumferential direction between the support plate 5c and the locking plate 8c each formed in the shape of a ring. (Book) supporting shafts 4a and 4b. Of the plurality of support shafts 4a and 4b, both end portions of some support shafts 4a and 4a have the support plate 5
It is supported by c and the locking plate 8c so as not to be displaced. For example, as shown in FIG. 16 (A), three support shafts 4a and 4b are provided.
In the case of the structure having the above-mentioned structure, two support shafts 4 are adjacent to each other, and in the case of the structure having four support shafts 4a and 4b, they are located on the diametrically opposite sides, as shown in FIG.
a and 4a are connected to both ends of the support plate 5c and the locking plate 8c.
In addition, it is fixed so that it cannot be displaced. For this reason, these support plates 5
c and a predetermined portion of the locking plate 8c, the support shafts 4a,
Circular holes 41, 41 are formed so that the ends of 4a can be fitted without rattling.

On the other hand, both ends of the remaining support shafts 4b and 4b are supported by the support plate 5c and the locking plate 8c so as to be slightly displaceable in the circumferential direction. For example, in FIG.
One in the case of the structure having three support shafts 4a and 4b as shown in (A), and one in the case of the structure having four support shafts 4a and 4b as shown in FIG. Both ends of the two opposite support shafts 4b and 4b are supported by the support plate 5c and the locking plate 8c so as to be displaceable in the circumferential direction. For this reason, circular holes 42, 42 are formed in predetermined portions of the support plate 5c and the locking plate 8c so that the ends of the support shafts 4b, 4b can be fitted therein without rattling. And
Rectangular through holes 43, 43, which are long in the diametrical direction of the support plate 5c and the locking plate 8c, are formed at positions sandwiching the circular holes 42, 42 from both sides in the circumferential direction. Then, the portions between the through holes 43, 43 and the circular holes 42, 42 are narrow portions 44a, 44b which are elastically deformable.

Also in the case of the planetary gear rotation support device of the eighth embodiment configured as described above, some of the plurality of support shafts 4a and 4b and the remaining support shafts 4a and 4b, Four
and b are elastically displaceable relative to each other in the circumferential direction. Then, when a large load is applied to a portion corresponding to a part of the support shafts 4a (or 4b) due to a manufacturing error, an assembly error, or the like, the part of the support shafts 4a (or 4b) and the remaining support shafts 4a (or 4b). The distance from 4b (or 4a) in the circumferential direction is elastically displaced. Therefore, the part of the support shaft 4a (or 4
Not only b) but also the remaining support shaft 4b (or 4a) bears the load applied from the ring gear 2 or the sun gear 1 to the planet gears 3a, 3b. As a result, some support shafts 4a, 4a
It is possible to improve the durability of the planetary gear device as a whole, because a large load is not applied only to the gear.

In the illustrated embodiment, each of the narrow portions 4 is
4a and 44b, the width dimension W _44a of the narrow portion 44a on the support plate 5c side is narrowed, and the width dimension W _44b of the narrow portion 44b on the locking plate 8c side is wide (W _44a <W _44b ). . Therefore,
When loads of the same magnitude are applied to both ends of the support shafts 4b and 4b in the circumferential direction, the base end, which is the end on the support plate 5c side, is the end on the locking plate 8c side. It is easier to displace than the tip end. The reason why the support rigidity of both end portions of the support shafts 4b, 4b is made different between the base end portion and the tip end portion is as follows.

During the operation of the planetary gear device, each of the support shafts 4 is
A radial load is applied to a and b in the circumferential direction,
The radial loads tend to incline the support shafts 4a and 4b. On the other hand, the support plate 5 whose inner peripheral edge is supported
The supporting rigidity of c is sufficiently large, while the supporting shaft 4
The supporting rigidity of the locking plate 8c, which is formed by simply connecting the tip portions of a and 4b, is small. Therefore, the locking plate 8c is more likely to be displaced in the circumferential direction than the support plate 5c. Therefore, both end portions of the support shafts 4b, 4b are supported with the same rigidity, and
When a radial load is applied to the axially intermediate portions of b and 4b in the circumferential direction, the displacement amount on the locking plate 8c side becomes larger than the displacement amount on the support plate 5c side end portion. The difference in such displacement is
The support shafts 4 for the rotation centers of the planetary gears 3A, 3B.
tied to the inclination of b, 4b. This inclination is due to the contact pressure of the rolling surfaces of the rollers 12 and 12, the outer ring raceway 11 on the inner peripheral surfaces of the planetary gears 3A and 3B, and the inner ring raceway 10 (FIGS. 30 to 32) on the outer peripheral surfaces of the support shafts 4b and 4b. Leading to the extreme rise of
After all, it causes damage such as flaking at an early stage.

Therefore, in the case of the illustrated embodiment, the width W _44b of the narrow portion 44b on the locking plate 8c side is widened in order to increase the rigidity of the tip side which is easily displaced, and the base end which is difficult to displace. The width dimension W _44a of the narrow portion 44a on the support plate 5c side is narrowed in order to reduce the rigidity on the side. With this configuration, there is no large difference between the support rigidity on the base end side and the support rigidity on the tip end side of the support shafts 4b, 4b as a whole. As a result, during operation of the planetary gear device, the planetary gears 3A, 3B are
The support shafts 4b, 4b are not tilted with respect to the center of rotation, and the damage can be prevented. Incidentally, each support shaft 4
If the inclination of each support shaft 4b, 4b is so small as to be negligible due to the relationship between the support rigidity of each of the support shafts 4b, 4b and the radial load applied to each of these support shafts 4b, 4b, then both the narrow portions 44a, 4b.
4b width dimensions W _44b and W _44a are equal (W _44b = W
_44a ) You may.

Next, FIGS. 20 to 21 show the ninth to tenth embodiments of the present invention corresponding to the second aspect. In the eighth embodiment described above, the shapes of the through holes 43, 43 for forming the narrow portions 44a, 44b are oblong, whereas in the ninth embodiment shown in FIG. 20, these through holes are formed. 43 and 43 are circular, and elliptical in the eleventh embodiment shown in FIG. Other configurations and operations are similar to those of the above-described eighth embodiment.

22 to 23 show a twelfth embodiment of the present invention, which corresponds to the second aspect. In the case of this embodiment, both ends of the support shaft 4b are attached to the support plate 5c and the locking plate 8.
The circular hole 4 formed in a predetermined portion of the support plate 5c and the locking plate 8c for supporting the movable plate c in a displaceable manner in the circumferential direction.
Notches 45a that open at the outer peripheral edges of the plates 5c and 8c, respectively, at positions sandwiching 2 and 42 from both sides in the circumferential direction,
45b is formed. And each of these notches 45
The portions between a and 45b and the inner peripheral edge of each of the plates 5c and 8c are narrow portions 46a and 46b that are elastically deformable.

Also in the case of this embodiment, each of these narrow portions 46 is
Of the a and 46b, the width dimension W _46a of the narrow portion 46a on the support plate 5c side is narrow, and the width dimension W _46b of the narrow portion 46b on the locking plate 8c side is wide (W _46a <W _46b ). . Other configurations and operations are similar to those of the eighth embodiment described above.

24 to 25 show a thirteenth embodiment of the present invention corresponding to the second aspect. In the case of this embodiment, the support plate 5c is inserted so as to insert both end portions of the support shaft 4b.
And the inner diameters of the circular holes 42a formed in the locking plate 8c, the small diameter portions 47 formed at both ends of the support shaft 4b,
It is sufficiently larger than the outer diameter dimension of 47. And
The inner peripheral surfaces of the circular holes 42a, 42a and the small diameter portions 4 described above.
Elastic materials 48a and 48b such as metal, rubber, elastomer, and synthetic resin are sandwiched between the outer peripheral surfaces of 7 and 47 in an elastically compressed state. In the case of the present embodiment, both ends of the support shaft 4b are supported by the support plate 5c and the locking plate 8c by the elastic members 48a and 48b so as to be elastically displaceable in the circumferential direction.

In the case of this embodiment, each of the elastic members 48 described above is used.
By forming the flat surfaces 49a and 49b on both sides of the a and 48b in the circumferential direction, the small-diameter portions 47 and 47 are smoothly displaced in the circumferential direction. In particular, in the illustrated embodiment, by widening the flat surfaces 49a, 49a on the side of the elastic member 48a to be mounted in the circular hole 42a on the side of the support plate 5c, the base end side of the support shaft 4b is displaced compared to the front end side. Making it easier. Other configurations and operations are similar to those of the eighth embodiment described above.

26 to 27 show a fourteenth embodiment of the present invention corresponding to the second aspect. In the case of the present embodiment, the outer peripheral surfaces of the elastic members 48a, 48b mounted between the inner peripheral surfaces of the circular holes 42a, 42a and the outer peripheral surfaces of the small diameter portions 47, 47 formed at both ends of the support shaft 4b. , Four flat surfaces 49a and 49b are formed. Other configurations and operations are similar to those of the thirteenth embodiment described above.

Next, FIG. 28 shows a fifteenth embodiment of the present invention corresponding to claim 2. In the case of the present embodiment, the inner peripheral surface of the circular hole 42a and the small diameter portion 4 at both ends of the support shaft 4b.
The elastic cylinder 52 is sandwiched between the outer peripheral surface of the elastic cylinder 52 and the outer peripheral surface of the elastic cylinder 52. The elastic cylinder 52 is formed by concentrically combining a metal sleeve 50 and an elastic material 51 such as rubber, elastomer, or synthetic resin. In the case of this embodiment, when the support rigidity of both ends of the support shaft 4b is changed, the material or thickness of the elastic member 51 is changed. Other configurations and operations are similar to those of the thirteenth embodiment described above.

Next, FIG. 29 shows a sixteenth embodiment of the present invention corresponding to claim 2. In the case of the present embodiment, the inner peripheral surface of the circular hole 42a and the small diameter portion 4 at both ends of the support shaft 4b.
An elastic tube 53 is sandwiched between the outer peripheral surface of the elastic tube 53 and the outer peripheral surface of the elastic tube 53. The elastic cylinder 53 includes a metal sleeve 54 and the sleeve 5.
4. Metal rod springs 55, 5 welded and fixed to the opening end of No. 4
It consists of 5 and. In the case of this embodiment, when changing the support rigidity of both ends of the support shaft 4b, the rod springs 55, 55 are used.
Change the hardness or wire diameter. Other configurations and operations are similar to those of the thirteenth embodiment described above. The elastic cylinder having the shape shown in FIG. 29 may be formed by a plate spring instead of the rod spring. In this case, a plurality of (preferably 3 to 4) leaf springs are supported inside the cylindrical sleeve, and the end portion of the support shaft is supported inside the leaf springs. When changing the support rigidity, the thickness and material of the leaf spring or the length dimension of the sleeve in the axial direction is changed.

[0046]

The rotation support device for a planetary gear of the present invention is constructed and operates as described above, but has a structure capable of transmitting a large amount of power which can be used as a transmission for an automobile, and particularly, has a high degree of precision in parts and assembly. Even if it is not raised, a large load will not be applied only to some of the support shafts. As a result, a planetary gear device having sufficient reliability and durability can be provided at low cost.

[Brief description of drawings]

FIG. 1 is a partially cut front view showing a first embodiment of the present invention.

FIG. 2 is a side view showing a right side of FIG. 1 with a part cut away.

FIG. 3 is a partial front view showing a planetary gear meshed with a sun gear and a ring gear.

4 is a sectional view taken along line AA of FIG.

FIG. 5 is a sectional view taken along line BB of FIG. 4;

FIG. 6 shows a deformed state when only a part of the planetary gears receives a large load, FIG. 6 (A) being similar to FIG. 4 and FIG. 5 (B) being similar to FIG.

FIG. 7 is a view similar to FIG. 4, showing a second embodiment of the present invention.

FIG. 8 is a view similar to FIG. 5 showing the third embodiment.

FIG. 9 is a view similar to FIG. 5 showing the fourth embodiment.

FIG. 10 is a view similar to FIG. 4 showing the fifth embodiment.

FIG. 11 is a view similar to FIG. 4 showing the sixth embodiment.

FIG. 12 is a front view showing the seventh embodiment.

13 is a cross-sectional view taken along line CC of FIG.

FIG. 14 is a front view showing an elastically deformed state of the elastic connecting piece.

FIG. 15 is a partial front view showing a planetary gear meshed with a sun gear and a ring gear.

FIG. 16 is a schematic front view showing an eighth embodiment of the present invention.

FIG. 17 is an enlarged view of part D in FIG.

18 is a cross-sectional view taken along line EE of FIG.

19A and 19B are views showing the shapes of a through hole and a narrow portion, FIG. 19A being a view as seen from an arrow F of FIG. 18, and FIG.

FIG. 20 is a view similar to FIG. 19 showing a ninth embodiment of the present invention.

FIG. 21 is a view similar to FIG. 19 showing a tenth embodiment of the present invention.

FIG. 22 is a schematic front view showing an eleventh embodiment of the present invention.

FIG. 23 shows a twelfth embodiment of the present invention, (A)
22B is a view corresponding to an enlarged view of the H part in FIG. 22, and FIG. 23B is a view of the H part viewed from the back surface side.

FIG. 24 is a partial sectional view showing a thirteenth embodiment of the present invention.

25A is a view from the left side of FIG. 24, and FIG. 25B is a right view of the same.

FIG. 26 is a partial sectional view showing a fourteenth embodiment of the present invention.

27A is a view from the left side of FIG. 26, and FIG.

FIG. 28 is a partial sectional view showing a fifteenth embodiment of the present invention.

FIG. 29 is a partial sectional view showing the sixteenth embodiment.

FIG. 30 is a partial cross-sectional view showing a first example of a conventional structure.

FIG. 31 is an enlarged cross-sectional view of the main part of the same.

32 is a cross-sectional view taken along the line I-I of FIG. 31.

FIG. 33 is a partial cross-sectional view showing a second example of the conventional structure.

[Explanation of symbols]

 1 sun gear 1a tooth 2 ring gear 2a tooth 3, 3A, 3B planetary gear 3a tooth 4, 4a, 4b support shaft 5, 5a, 5b, 5c support plate 6 cylindrical portion 7 rotary shaft 8, 8a, 8b, 8c locking Plate 9 Circle hole 10 Inner ring raceway 11 Outer ring raceway 12 Roller 13 Oil passage hole 14 Inner race 15 Annular gap 16 Oil film layer 17 First support plate element 18 Second support plate element 19 Female spline groove 20 Circle ring portion 21 Circle hole 22 Cylindrical part 23 1st locking plate element 24 2nd locking plate element 25 Circular hole 26 Cylindrical part 27 1st planetary gear carrier 28 2nd planetary gear carrier 29 Connecting pin 30a, 30b, 31a, 31b Circle Hole 32 Through hole 33 Narrow portion 34 Elastic material 35 Elastic connecting piece 36 First connecting pin 37 Second connecting pin 38 Through hole 39 Locking hole 40 Elastic deforming portion 41, 42, 42a Circular hole 4 Holes 44a, 44b narrow portions 45a, 45b notch 46a, 46b narrow section 47 the small diameter portion 48a, 48b elastic members 49a, 49b flat surface 50 the sleeve 51 an elastic member 52, 53 flexible tubular 54 sleeve 55 rod spring

Claims (2)

[Claims] 1. A support plate and a locking plate, which have rotation centers coinciding with each other and are arranged in parallel to each other, and are arranged in parallel to the rotation center and on the same arc centered on the rotation center. For a planetary gear including a plurality of support shafts having both ends supported by the support plate and the locking plate, and a plurality of planetary gears rotatably supported around the middle portion of each support shaft. In the rotation support device, the support plate is composed of a first support plate element and a second support plate element which are movably combined with each other in the circumferential direction, and the locking plates are It is composed of a first locking plate element and a second locking plate element that are displaceably combined in the circumferential direction, and both ends of a part of the support shafts of the plurality of support shafts are Supported by the first support plate element and the first locking plate element, the plurality of the plurality of It constitutes a first planetary gear carrier that rotatably and revolvably supports a part of the planetary gears, and both ends of the remaining supporting shafts of the plurality of supporting shafts are the second planetary gear carriers. Is supported by the support plate element and the second locking plate element, and constitutes a second planetary gear carrier that rotatably and revolvably supports the remaining planetary gears of the plurality of planetary gears. An elastic displacement portion is provided between the first planetary gear carrier and the second planetary gear carrier, which serves as a resistance against relative displacement between the two planetary gear carriers in the circumferential direction. A rotation support device for planetary gears that is characterized. 2. A support plate and a locking plate, which have rotation centers coinciding with each other and are arranged in parallel with each other, and are arranged in parallel with the rotation center and on the same arc centered on the rotation center. For a planetary gear including a plurality of support shafts having both ends supported by the support plate and the locking plate, and a plurality of planetary gears rotatably supported around the middle portion of each support shaft. In the rotary support device, both ends of a part of the support shafts of the plurality of support shafts are non-displaceably supported by the support plate and the locking plate, and the rest of the plurality of support shafts. Both ends of the support shaft of the planetary gear are supported by the support plate and the locking plate so as to be elastically displaceable in the circumferential direction.