JPH07317885A - Rotation support device for planetary gear - Google Patents

Abstract

PURPOSE:To reduce the occurrence of resistance against the flow of lubricating oil by a method wherein the thickness in an axial direction of the part, closer to an inner peripheral edge, of spacer is decreased to a value lower than the thickness in an axial direction of a part with which the end faces of rollers arranged in a plurality of rows are brought into contact. CONSTITUTION:Slopes 30 inclined in a reverse direction to each other are formed at the parts, closer to an inner peripheral edge, of the two end faces in an axial direction of a spacer 23a. Based on the slope 30, the thickness in an axial direction of the part, closer to an inner peripheral edge, of the spacer 23a is decreased toward the inner peripheral edge. The width (w) of the inner peripheral edge of the spacer 23a is decreased to a value lower than the diameter D of the opening of the nozzle hole 27, Further, the end face of each roller 21 is brought into contact with a part closer to an outer periphery than each slope 30 and having a sufficiently high thickness. This constitution feeds a sufficient amount of lubricating oil to the rolling surface of each roller 21 and a contact part between inner and outer wheel orbits 19 and 20, reduces the occurrence of wear, and the occurrence of a trouble, such as seizure.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION A planetary gear rotation supporting device according to the present invention rotatably supports a planetary gear incorporated in a planetary gear device constituting an automatic transmission or a transaxle for an automobile around a support shaft. To use for.

[0002]

2. Description of the Related Art A planetary gear unit constituting an automatic transmission for a vehicle is constructed as shown in FIGS. The input shaft 1 is rotatably supported by a bearing 2 inside a housing 3. The rotation of the input shaft 1 is transmitted to the support plate 5 via the hub 4. In this support plate 5,
The base ends of a plurality of support shafts 6, 6 arranged concentrically around the input shaft 1 are fitted and fixed. The planetary gears 7, 7 are rotatably supported around the intermediate portions of the support shafts 6, 6 via roller bearings 8, 8, respectively.

That is, as shown in detail in FIG. 15, the cylindrical inner ring raceway 19 formed on the outer peripheral surface of the intermediate portion of each of the support shafts 6 and the inner peripheral surface of each of the planetary gears 7 and 7. A plurality of rollers 21 and 21 are rotatably arranged between the outer ring raceway 20 and the outer ring raceway 20 formed in the cylindrical shape. The planetary gears 7, 7 rotate around the support shafts 6, 6 based on the rolling of the plurality of rollers 21, 21. or,
A spacer 23 is provided at an intermediate portion of a space 22 between the inner ring raceway 19 and the outer ring raceway 20. The spacer 23 is made of metal, synthetic resin, or the like, and is formed in an annular shape having a rectangular cross section as shown in FIG. When the above two or more
1, 21 are arranged in multiple rows with the spacer 23 interposed therebetween.

Inside the support plate 5 and the support shafts 6 and 6, oil supply passages 24 and 25 which communicate with each other are provided. The oil supply passages 24 and 25 communicate with the main oil supply passage 26 formed at the center of the input shaft 1 via the hub 4.
Further, a nozzle hole 27 is formed in the diametrical direction in the middle portion of each of the support shafts 6, 6. One end (upper end in FIG. 15) of the nozzle hole 27 communicates with the oil supply passage 25 formed in the center of the support shaft 6, and the other end (lower end in FIG. 15) is the outer peripheral surface of the intermediate portion of the support shaft 6. The opening is formed in a portion facing the inner peripheral edge of the spacer 23.

An oil supply passage 2 formed at the center of the support shaft 6
The tip of 5 (the left end in FIG. 15) is closed by a plug 28. Further, a connection portion 25a extending in the diametrical direction (vertical direction in FIG. 15) is formed at the base end portion (right end portion in FIG. 15) of the oil supply passage 25. Then, with this connecting portion 25a,
The support plate 5 is aligned with the oil supply passage 24 formed in the diametrical direction so that the two oil supply passages 24, 25 are communicated with each other. Further, the pin 29 inserted from the diametrically outer end of the oil supply passage 24 is press-fitted into the end of the connecting portion 25a. The pin 29 is connected to one end of the connecting portion 25a (see FIG. 15).
The upper end of the opening is closed so that all the lubricating oil fed from the oil supply passage 24 is fed to the nozzle hole 27, and the support shaft 6 is prevented from rotating with respect to the support plate 5.

Further, the tips of the support shafts 6, 6 (see FIG. 15).
The left end) of the support shaft 6 is fitted and fixed to a connecting plate 9 formed in a ring shape, and the tip ends of the support shafts 6, 6 are connected to each other. Then, as shown in FIG. 15, thrusts are respectively provided between both end faces of the planetary gears 7, 7 in the axial direction (the left-right direction in FIG. 14) and the inner side faces of the support plate 5 and the connecting plate 9, respectively. Washers 17, 18 are provided. Each of these thrust washers 17, 18 is made of metal and formed in a ring shape as shown in FIG. These thrust washers 17, 18 are
The planetary gears 7, 7 are prevented from rubbing against the inner surfaces of the supporting plate 5 and the connecting plate 9, and the end faces of the rollers 21, 21 constituting the roller bearings 8, 8 are supported by the supporting members. It is possible to prevent the inner surfaces of the plate 5 and the connecting plate 9 from being scraped.

On the other hand, around the input shaft 1, inside the planetary gears 7, 7, a cylindrical sun gear 10 is rotated with respect to the input shaft 1 via another roller bearing 11, 11. It is provided freely. The sun gear 10 and the planetary gears 7, 7 are meshed with each other. A thrust bearing 13 is provided between the boss 12 of the sun gear 10 and the connecting plate 9.

Further, an output gear 14 is provided around the hub 4.
The pair of tapered roller bearings 15 and 15 rotatably support the hub 4. The ring gear 1 is attached to one side surface (left side surface in FIG. 14) of the output gear 14.
6, the ring gear 16 and the planetary gears 7,
It meshes with 7.

In the planetary gear device configured as described above, the rotation speed ratio between the input shaft 1 and the output gear 14 can be changed by switching the rotation states of the sun gear 10 and the ring gear 16, for example. it can. Also, during operation of the automatic transmission incorporating the planetary gear device, the lubricating oil sent from the pump (not shown) into the main oil supply passage 26 is sent to the nozzle hole 27 via the oil supply passages 24 and 25. Be done. Then, the lubricating oil is discharged from the nozzle hole 27 into the space 22 between the inner ring raceway 19 and the outer ring raceway 20,
The raceways 19, 20 and the rolling surfaces of the rollers 21, 21 are lubricated.

Each of the tracks 19 and 20 and a plurality of rollers 21,
After lubricating the rolling surface of 21, the lubricating oil is applied between the side surfaces of the thrust washers 17, 18 and the side surfaces of the thrust washers 17, 18 and the supporting plate 5 and the connecting plate 9. It passes through a gap between the inner surface or both end surfaces of the planetary gear 7 and flows out of the space 22. Then, the lubricating oil that has flowed out of the space 22 is again sucked by the pump and used for lubrication of each part of the automatic transmission.

[0011]

However, in the conventional rotation supporting device for the planetary gears, when the conditions are strict, the portion that needs lubrication, that is, the inner ring raceway 19 and the outer ring raceway 20 and the plurality of rollers. 21, 21, the contact portion with the rolling surface,
Also, there is a possibility that the installation portions of the thrust washers 17, 18 may not be sufficiently lubricated between the both end surfaces of the planetary gear 7 and the inner surfaces of the support plate 5 and the connecting plate 9. That is, in the case of an automatic transmission for automobiles that incorporates a planetary gear device, the lubricating oil (also used as automatic fluid) stored in the transmission case is pumped by a pump to each portion that requires lubrication, but the rotation of the planetary gear 7 The support is located at the end of the hydraulic circuit for supplying the lubricating oil. Further, this hydraulic circuit is branched into a plurality of parts on the way, and there are a plurality of ends.

Therefore, if the resistance against the flow of the lubricating oil increases in the planetary gear rotary support portion, which is the terminal portion, the lubricating oil flows more to the other terminal portions, and the amount flowing to the terminal portion having the higher resistance decreases. I will end up. In addition, the increase in the resistance at the end portion increases the back pressure of the pump and increases the power required to drive the pump, which causes the performance of an automatic transmission or the like incorporating a planetary gear device to deteriorate. Become. Therefore, in order to sufficiently lubricate the rotation support portion for the planetary gears and to improve the performance of the automatic transmission and the like, the resistance of the plurality of rotation support portions for the planetary gears (with respect to passage of lubricating oil) is increased. Needs to be small. However, in the case of the conventional rotation support device for planetary gears, the following
Due to the above reasons, the resistance of the rotary support device portion was not always small.

Since the opening of the nozzle hole 27 is close to the inner peripheral edge of the spacer 23, the flow passage area between the nozzle hole 27 and the space 22 is narrow. That is, in the case of the conventional structure, as shown in FIG. 15, the inner diameter of the spacer 23 is only slightly larger than the outer diameter of the support shaft 6, and the inner peripheral edge of the spacer 23 is the nozzle hole 27. Was facing the opening. For this reason, most of the openings of the nozzle holes 23 are the spacers 2.
It was blocked by No. 3, the flow passage area was narrowed, and the resistance against the flow of lubricating oil was increased.

Since the width of the lubricating oil flow path at which the washers 17 and 18 are installed is narrow and long, it is difficult for the lubricating oil to flow. As a result, the space between the side surfaces of the thrust washers 17, 18 and the thrust washers 17, 1, respectively.
It becomes difficult for a sufficient amount of lubricating oil to be fed into the gap between the side surface of No. 8 and the inner surface of the support plate 5 and the connecting plate 9 or both end surfaces of the planetary gear 7. As a result, the parts where the thrust washers 17, 18 are installed are insufficiently lubricated,
Not only may seizure occur in this portion, but also the replacement of the lubricating oil in the space 22 becomes defective. As a result, the lubrication between the inner ring raceway 19 and the outer ring raceway 20 and the rolling surfaces of the plurality of rollers 21, 21 also becomes poor.

The lubricating oil that has entered the oil supply passage 25 provided in the center of the support shaft 6 from the oil supply passage 24 provided in the support plate 5 is not always effectively fed into the nozzle hole 27. As a result, the lubricating oil stays in the oil supply passages 25 and the resistance in the oil supply passages 24, 25 increases. As a result,
There is a possibility that the lubricating oil supplied to the space 22 or the installation portion of the thrust washers 17, 18 may be insufficient.

The planetary gear rotation support device of the present invention eliminates at least one of the causes (1) to (3) to reduce the resistance to the flow of lubricating oil, and to lubricate each part requiring lubrication in a sufficient amount. It makes it possible to send oil.

[0017]

In any of the rotation supporting devices for planetary gears of the present invention, a supporting plate and one end thereof are supported and fixed to the supporting plate, and the outer peripheral surface of the intermediate part is a cylindrical inner ring raceway. A support shaft and teeth are formed on the outer peripheral surface, and a cylindrical outer ring raceway is formed on the inner peripheral surface. The support shaft is rotatably provided around the support shaft, and the ring gear is provided on the outer side and the ring gear is provided on the inner side. A planetary gear meshing with the sun gear, and a plurality of rollers rotatably provided between the inner ring raceway and the outer ring raceway,
An oil supply passage provided inside the support plate and the support shaft and communicating with each other, and a nozzle hole having one end communicated with the oil supply passage and the other end opened on the outer peripheral surface of the intermediate portion of the support shaft. ing.

In the planetary gear rotation support device according to the first and second aspects, an annular spacer is provided on the inner peripheral surface of the middle portion of the outer ring raceway, and the inner ring raceway and the outer ring raceway are provided. A plurality of rollers are arranged in double rows between the raceway and the raceway, and the other end of the nozzle hole is opened in a portion facing the inner peripheral edge of the raceway.

Particularly, in the planetary gear rotation support device according to the first aspect of the invention, the axial thickness of the inner peripheral edge portion of the spacer is arranged in the double row in the main body portion of the spacer. It is smaller than the axial thickness of the part where the end face of the roller contacts.

Further, in the planetary gear rotation support device according to the second aspect, the diametrical thickness of the spacer is smaller than half the distance between the inner ring raceway and the outer ring raceway, and There is a sufficiently large gap between the inner peripheral edge and the opening of the nozzle hole.

In addition, in the planetary gear rotation support device according to the third aspect, a thrust washer is provided between the side surface of the support plate and the axial end surface of the planet gear. Particularly, in the planetary gear rotation support device according to the third aspect of the present invention, the thrust washer is provided with a concave groove having a diametrical curvature on at least one surface thereof.

Furthermore, in the planetary gear rotation support device according to the fourth aspect, the oil supply passage provided in the support shaft is a tapered hole whose inner diameter increases as the distance from the support plate increases. .

[0023]

In the case of the rotation supporting device for a planetary gear device of the present invention configured as described above, the resistance against the flow of lubricating oil can be reduced, and sufficient lubricating oil can be supplied to the necessary portions.

First, in the case of the rotation supporting device for the planetary gear device according to the first and second aspects, a large lubricating oil passage having a sufficiently large area is provided between the inner peripheral edge of the spacer and the opening of the nozzle hole. It is formed. Therefore, the cause of the increase in resistance at the nozzle hole opening as described above is eliminated.

Further, in the case of the planetary gear device rotary support device according to the third aspect of the present invention, since the concave groove functions as a pump and a sufficient amount of lubricating oil flows through the concave groove, the thrust washer as described above is used. The cause of the increase in resistance at the installation part is eliminated.

Further, in the case of the planetary gear device rotation support device according to the fourth aspect, the lubricating oil that has entered the oil supply passage flows in a direction away from the support plate by centrifugal force based on the revolution movement of the support shaft. . Therefore, the flow of the lubricating oil in the oil supply passage becomes smooth, and the above-mentioned cause of the increase in resistance in the oil supply passage is eliminated.

[0027]

1 and 2 show a first embodiment of the present invention corresponding to claim 1. Incidentally, the same parts as those of the conventional structure described above are designated by the same reference numerals to omit redundant description, and hereinafter, the characteristic part of the present invention will be mainly described.

The spacer 23a, which is disposed in the middle portion of the space 22 in the axial direction (left-right direction in FIG. 1) and divides the rollers 21 arranged in a plurality of rows, is made of metal into an annular shape as shown in FIG. Has been formed. The spacer 23a has an outer diameter equal to or slightly smaller than the diameter of the outer ring raceway 20 and an inner diameter larger than the diameter of the inner ring raceway 19.

Further, on the inner peripheral edge portions of both end surfaces of the spacer 23a in the axial direction, inclined surfaces 30 and 3 inclined in opposite directions are provided.
Forming 0. Due to the presence of the inclined surfaces 30, 30, the axial thickness of the portion of the spacer 23a near the inner peripheral edge becomes smaller toward the inner peripheral edge. The width w of the inner peripheral edge of the spacer 23a is sufficiently smaller than the diameter d of the opening of the nozzle hole 27 (w << d).
The end surfaces of the rollers 21 and 21 have the inclined surfaces 30 and 3 respectively.
It contacts the portion having a thickness dimension sufficiently larger than the outer peripheral portion than zero. Therefore, even if the end faces of the rollers 21, 21 collide with the side surface of the spacer 23a as the planetary gear 7 rotates, the strength of the spacer 23a is sufficiently secured.

In the case of the rotation supporting device for the planetary gear device of the present invention configured as described above, a sufficiently large area with a large lubrication is provided between the inner peripheral edge of the spacer 23a and the opening of the nozzle hole 27. An oil flow path is formed. Therefore, the lubricating oil discharged from the nozzle hole 27 flows into the space 22 in which the rollers 21 and 21 are arranged without particularly restricting the flow passage. Therefore, the rolling surfaces of these rollers 21, 21 and the inner ring raceway 1
A sufficient amount of lubricating oil can be sent to the abutting portion with the outer raceway 9 and the outer ring raceway 20.

Next, FIGS. 3 to 5 correspond to claim 2.
2 shows a second embodiment of the present invention. In the case of the present embodiment, the thickness T of the spacer 23b for partitioning the rollers 21, 21 arranged in multiple rows in the diameter direction (vertical direction in FIGS. 3 to 4).
Is less than half the distance D between the inner ring raceway 19 and the outer ring raceway 20 (T ≦ D / 2), which is sufficiently small. That is, the outer diameter of the spacer 23b is slightly smaller than the diameter of the outer ring raceway 20, and the inner diameter of the spacer 23b is sufficiently larger than the diameter of the inner ring raceway 19. Therefore, there is a sufficiently large gap between the inner peripheral edge of the spacer 23b and the opening of the nozzle hole 27.

Also in the case of the present embodiment, as in the case of the above-mentioned first embodiment, the strength of the spacer 23b is ensured, and the space between the inner peripheral edge of the spacer 23b and the opening of the nozzle hole 27 is sufficient. A large lubricating oil flow path is formed in the
1, 21 rolling surfaces and the inner ring raceway 19 and outer ring raceway 20
Sufficient amount of lubricating oil can be sent to the contact part with.

Next, FIGS. 6 to 8 correspond to claim 2,
3 shows a third embodiment of the present invention. In the case of this embodiment, both axial end faces of the rollers 21a, 21a arranged in double rows are not spherical but flat. In accordance with this, the shape of the spacer 23c is changed. That is, in the case of the present embodiment, the thickness T'of the spacer 23c across the diameter is made smaller than that of the second embodiment described above. Each time 21
Since both axial end faces of a and 21a are flat, even if the thickness T'of the spacer 23c is reduced, it is possible to reliably prevent the rollers 21a and 21a arranged in double rows from colliding with each other. it can. Other configurations and operations are similar to those of the above-described second embodiment.

Next, FIGS. 9 to 10 show a fourth embodiment of the present invention, which corresponds to the third aspect. In the case of the present embodiment, the cylindrical parts 31, 31 projecting to the outer surface side are formed on the inner peripheral edge portions of the thrust washers 18a, 18a provided on the support plate 5 and the connecting plate 9 sides. And each cylindrical portion 3
1, 31 are fitted in the recesses 32, 32 formed on the inner side surfaces of the support plate 5 and the connecting plate 9 to prevent the thrust washers 18a, 18a from rotating.

Further, each of these thrust washers 18a, 1
On the inner surface of 8a, a concave groove 3 having a diametrical curvature is formed.
A plurality of 3, 33 are formed. In the illustrated embodiment, these concave grooves 33, 33 are arc-shaped dynamic pressure grooves that are inclined in the circumferential direction and are displaced in the diametrical direction.

In the case of the rotation support device for the planetary gear device of the present embodiment, the pump action of the concave grooves 33, 33 formed on the inner side surfaces of the thrust washers 18a, 18a causes the concave grooves 33, 33 to pass through the concave grooves 33, 33, respectively. A sufficient amount of lubricating oil flows from the space 22 toward the periphery of the planetary gear 7. Therefore, the resistance to the circulation of the lubricating oil does not increase at the installation positions of the thrust washers 18a and 17.

Particularly, in the illustrated embodiment, since the concave grooves 33, 33 are dynamic pressure grooves, when the thrust washers 17, 17 rotate together with the planetary gear 7, the thrust washers 17, 17 are rotated. Dynamic pressure is generated between the outer side surface of 17 and the inner side surfaces of the thrust washers 18a, 18a, and the side surfaces of the thrust washers 17, 18a are reliably separated from each other. As a result, the friction resistance of the thrust washer 17, 18a installation portion is sufficiently reduced.

When carrying out the invention described in claim 3, it is not always necessary to use the concave groove as a dynamic pressure groove. or,
It is also possible to provide only one thrust washer between both end surfaces of the planetary gear 7 and the inner side surfaces of the support plate 6 and the connecting plate 9, and to form a plurality of recessed grooves on both sides of the thrust washer.

Next, FIGS. 11 to 12 show a fifth embodiment of the present invention, which corresponds to the fourth aspect. In the case of the present embodiment, the oil supply passage 25A provided in the support shaft 6 is a tapered hole whose inner diameter increases as the distance from the support plate 5 increases. Further, the plug 28 is pushed in close to the nozzle hole 27.

In the case of the rotation support device for the planetary gear device of the present embodiment, the oil supply passage 2 is formed by the centrifugal force based on the revolution movement of the support shaft 6 around the input shaft 1 (FIG. 14).
The lubricating oil that has entered into 5A flows in a direction away from the support plate 5 (leftward in FIGS. 11 to 12). Therefore, the flow of the lubricating oil in the oil supply passage 25A becomes smooth, the lubricating oil does not stay in the oil supply passage 25A, and the resistance does not increase in the oil supply passage 25A.

In the case of the illustrated embodiment, the nozzle hole 2
7 is provided on the diametrically inner side of the support shaft 6, but if it is provided on the diametrically outer side, the flow of the lubricating oil due to the revolution movement can be made smoother and the flow resistance can be reduced.

Further, the inventions described in claims 1 to 4 can obtain a certain effect even if they are independently implemented.
However, by carrying out in combination, it is possible to further reduce the flow resistance of the lubricating oil and improve the lubricity of the planetary gear rotation supporting device. For example, FIG. 13 shows a sixth embodiment of the present invention, which is a combination of the inventions described in claims 1, 3, and 4. In this way, by combining a plurality of inventions, a sufficient amount of lubricating oil is circulated to each part of the planetary gear rotation supporting device, and even if the conditions are severe such as insufficient lubricating oil, a failure such as seizure may occur. Can be prevented more reliably.

[0043]

Since the rotation support device for a planetary gear of the present invention is constructed and operates as described above, it is possible to feed a sufficient amount of lubricating oil to a necessary portion, reduce wear, seizure, etc. Failure can be prevented, and durability and reliability of various mechanical devices including a planetary gear device such as an automatic transmission for automobiles can be improved.

[Brief description of drawings]

FIG. 1 is a sectional view of a main part showing a first embodiment of the present invention.

FIG. 2 shows a spacer used in the first embodiment,
(A) is a front view and (B) is a side view.

FIG. 3 is a sectional view of a main part, showing the second embodiment of the present invention.

FIG. 4 is an enlarged view of part A in FIG.

FIG. 5 shows a spacer used in the second embodiment,
(A) is a front view and (B) is a side view.

FIG. 6 is a sectional view of a main part, showing a third embodiment of the present invention.

FIG. 7 is an enlarged view of a part B in FIG.

FIG. 8 shows a spacer used in the third embodiment,
(A) is a front view and (B) is a side view.

FIG. 9 is a sectional view of a main part, showing a fourth embodiment of the present invention.

FIG. 10 shows a thrust washer used in the fourth embodiment, (A) is a front view and (B) is a side view.

FIG. 11 is a sectional view of a main part, showing a fifth embodiment of the present invention.

FIG. 12 is a sectional view showing the support shaft only.

FIG. 13 is a cross-sectional view of an essential part showing a sixth embodiment of the present invention.

FIG. 14 is a sectional view of an essential part showing an example of a planetary gear device.

FIG. 15 is a sectional view of an essential part showing an example of a conventional structure.

FIG. 16 shows a spacer incorporated in a conventional structure, (A) is a front view and (B) is a side view.

FIG. 17 shows a thrust washer incorporated in a conventional structure, (A) is a front view and (B) is a side view.

[Explanation of symbols]

 1 Input Shaft 2 Bearing 3 Housing 4 Hub 5 Support Plate 6 Support Shaft 7 Planetary Gear 8 Roller Bearing 9 Connecting Plate 10 Sun Gear 11 Roller Bearing 12 Boss 13 Thrust Bearing 14 Output Gear 15 Tapered Roller Bearing 16 Ring Gear 17, 18, 18a Thrust washer 19 Inner ring raceway 20 Outer ring raceway 21, 21a Roller 22 Space 23, 23a, 23b, 23c Spacer 24, 25, 25A Oil supply passage 25a Connection part 26 Main oil supply passage 27 Nozzle hole 28 Plug 29 Pin 30 Sloping surface 31 Cylindrical Part 32 Recessed part 33 Recessed groove

Claims (4)

[Claims] 1. A support plate, a support shaft whose one end is supported and fixed to the support plate, and an outer peripheral surface of an intermediate portion is an inner ring raceway of a cylindrical surface, teeth are formed on the outer peripheral surface, and a cylindrical surface is formed on the inner peripheral surface. Outer ring orbit of
A planetary gear that is formed around each of the support shafts and is rotatably provided around the support shaft and meshes with a ring gear provided on the outer side and a sun gear provided on the inner side, and rolling between the inner ring raceway and the outer ring raceway. A plurality of freely provided rollers, an oil supply passage provided inside the support plate and the support shaft and communicating with each other, and one end thereof communicated with the oil supply passage, and an outer peripheral surface of the intermediate portion of the support shaft. A nozzle hole having the other end opened, and an annular spacer is provided on the inner peripheral surface of the intermediate portion of the outer ring raceway, and the inner ring raceway and the outer ring raceway are each provided with this spacer. In the planetary gear rotation support device, in which a plurality of rollers are arranged in a double row, and the other end of the nozzle hole is opened in a portion facing the inner peripheral edge of the spacer, The axial thickness of the part near the inner peripheral edge is Part rotating support apparatus planetary gear, characterized in that the end face of the roller arranged in the double-row is smaller than the axial thickness of the abutting portion. 2. A support plate, a support shaft whose one end is supported and fixed to the support plate, and an outer peripheral surface of an intermediate portion is a cylindrical inner ring raceway, a tooth is formed on the outer peripheral surface, and a cylindrical surface is formed on the inner peripheral surface. Outer ring orbit of
A planetary gear that is formed around each of the support shafts and is rotatably provided around the support shaft and meshes with a ring gear provided on the outer side and a sun gear provided on the inner side, and rolling between the inner ring raceway and the outer ring raceway. A plurality of freely provided rollers, an oil supply passage provided inside the support plate and the support shaft and communicating with each other, and one end thereof communicated with the oil supply passage, and an outer peripheral surface of an intermediate portion of the support shaft. A nozzle hole having an opening at the other end is provided, and an annular spacer is provided on the inner peripheral surface of the middle portion of the outer ring raceway, and between the inner ring raceway and the outer ring raceway, the spacers are respectively interposed. In the planetary gear rotation support device, in which a plurality of rollers are arranged in a double row, and the other end of the nozzle hole is opened in a portion facing the inner peripheral edge of the spacer, Between the inner ring raceway and the outer ring raceway whose diametrical thickness is between Of less than half, the rotating support device planetary gear, characterized in that there is a large gap sufficiently between the opening of the inner peripheral edge and the nozzle hole of the spacer. 3. A support plate, a support shaft whose one end is supported and fixed to the support plate, and an outer peripheral surface of an intermediate portion is a cylindrical inner ring raceway, teeth are formed on the outer peripheral surface, and a cylindrical surface is formed on the inner peripheral surface. Outer ring orbit of
A planetary gear that is formed around each of the support shafts and is rotatably provided around the support shaft and meshes with a ring gear provided on the outer side and a sun gear provided on the inner side, and rolling between the inner ring raceway and the outer ring raceway. A plurality of freely provided rollers, an oil supply passage provided inside the support plate and the support shaft and communicating with each other, and one end thereof communicated with the oil supply passage, and an outer peripheral surface of an intermediate portion of the support shaft. In a planetary gear rotation supporting device having a nozzle hole with the other end opened, and a thrust washer provided between the side surface of the support plate and the axial end surface of the planetary gear, the thrust washer A rotation supporting device for a planetary gear, characterized in that a concave groove having a curvature in a diametrical direction is formed on at least one surface. 4. A support plate, a support shaft whose one end is supported and fixed to the support plate, and an outer peripheral surface of the intermediate portion is a cylindrical inner ring raceway, and teeth are formed on the outer peripheral surface and a cylindrical surface is formed on the inner peripheral surface. Outer ring orbit of
A planetary gear that is formed around each of the support shafts and is rotatably provided around the support shaft and meshes with a ring gear provided on the outer side and a sun gear provided on the inner side, and rolling between the inner ring raceway and the outer ring raceway. A plurality of freely provided rollers, an oil supply passage provided inside the support plate and the support shaft and communicating with each other, and one end thereof communicated with the oil supply passage, and an outer peripheral surface of an intermediate portion of the support shaft. In a planetary gear rotation support device having a nozzle hole with the other end opened, an oil supply passage provided in the support shaft is a tapered hole whose inner diameter increases as the distance from the support plate increases. A rotation support device for planetary gears that is characterized.