JP2006220219A - Planetary gear device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a planetary gear device having reduced noises from a case by suppressing the transmission of meshing vibration from a pinion gear to the case. <P>SOLUTION: The planetary gear device 40 stored in the case 5 comprises a reversing brake 50 provided between a carrier 44 (45. 46) and a pump cover 8 as a stationary member. The pump cover 8 has a brake plate supporting portion 8a integrally formed to be spline-fitted with the outer periphery of a brake plate 50a. A gap δ is formed between the outer periphery of the brake plate supporting portion 8a and the inner periphery of the case 5. The mass effects of the pump cover 8 and a pump body 7 suppress the transmission of gear noises from the pinion gear 43 to the case 5. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

The present invention relates to a planetary gear device used for an automatic transmission or a continuously variable transmission, and more particularly to a structure for reducing gear noise.

Conventionally, in Patent Document 1, as a forward / reverse switching mechanism for a continuously variable transmission, a sun gear coupled to an input side, a ring gear coupled to an output side, and a forward brake for locking a carrier to a case, A single pinion type planetary gear device having a reverse clutch for connecting a carrier and a sun gear is disclosed. During forward travel, the forward brake is engaged and the reverse clutch is released, so that the driving force input from the input side is reversed and decelerated and transmitted to the output side. By releasing the brake, the input side and the output side are directly connected.

FIG. 6 shows the structure of the planetary gear device described in Patent Document 1.
The sun gear 101 of the planetary gear device 100 is coupled to the input shaft 102, and the pinion gear 103 that meshes with the sun gear 101 is supported by the carrier 105 via the pinion shaft 104. A disc-shaped carrier plate 106 is fixed to the front side of the carrier 105, and its inner diameter side is rotatably supported by the input shaft 102, and its outer diameter side is used as a brake hub 106a of the forward brake 107. A clutch bubb 106b of the reverse clutch 108 is fixed to the intermediate portion. A hydraulic piston 109 for fastening the clutch disk of the reverse clutch 108 is disposed in the clutch drum 110, and an inner peripheral end portion of the clutch drum 110 is connected to the input shaft 102. The hydraulic piston 111 that fastens the brake plate 107 a of the forward brake 107 is accommodated in a recess 113 formed on the inner wall of the transmission case 112. The inner diameter portion of the ring gear 114 that meshes with the pinion gear 103 is spline-fitted inside the pulley shaft 116 of the drive pulley 115.

As described above, the inner peripheral portion of the disk which is one of the brake plates 107a of the forward brake 107 is spline-fitted to the carrier 106a, and the outer peripheral portion of the plate which is the other of the brake plates 107a is spline-fitted to the case 112. Yes.
However, when the forward brake 107 is engaged during forward travel, the meshing vibration (gear sound) of the pinion gear 103 is transmitted from the carrier 106a to the case 112 via the brake plate 107a, and noise is generated from the case 112. There is.

The same problem as in Patent Document 1 also occurs in a planetary gear device as described in Patent Document 2.
This planetary gear device is a double pinion type, and includes a direct coupling clutch provided between the input shaft and the carrier, and a reverse brake provided between the ring gear and the transmission case. Coupled to the input shaft on the input side, the carrier is coupled to the drive pulley on the output side.
At the time of forward movement, by engaging the direct coupling clutch, the input shaft and the carrier are directly coupled, and the rotation of the input shaft is directly transmitted to the drive pulley. During reverse travel, the reverse gear brake is fastened to fix the ring gear and the transmission case, so that the rotation of the input shaft is reversed and transmitted to the drive pulley.

Also in this planetary gear unit, one of the brake plates of the reverse brake is directly splined to the case, so when the reverse brake is engaged during reverse travel, the meshing vibration (gear sound) of the pinion gear passes through the brake plate from the ring gear. Noise is generated from the case.
JP 2002-327828 A Japanese Patent Laid-Open No. 10-184834

Therefore, an object of the present invention is to provide a planetary gear device that can suppress the meshing vibration of the pinion gear from being transmitted to the case and reduce the noise generated from the case.

In order to achieve the above object, the invention described in claim 1 is a planetary gear device which is housed in a case and configured so that one rotating element can be fastened and released to a stationary member via a brake. The stationary member is an oil pump main body fixed to the case, and the oil pump main body is integrally formed with a brake plate support portion for spline supporting the outer peripheral side of the brake plate of the brake, and the brake plate support portion A planetary gear device is provided in which a gap is provided between the outer periphery of the case and the inner periphery of the case.

According to a second aspect of the present invention, there is provided a planetary gear device that is housed in a case and configured so that one rotating element can be fastened / released via a brake with respect to the stationary member. A drum-shaped part that supports the outer peripheral side of the brake plate by spline, and the drum-shaped part is joined to an oil pump main body fixed to the case via a vibration isolator, Provided is a planetary gear device characterized in that a gap is provided between the case and the inner periphery.

In claim 1, since the outer peripheral side of the brake plate is splined to the brake plate support portion of the oil pump main body, the meshing vibration (gear sound) of the pinion gear is applied to the oil pump main body via the brake when the brake is engaged. Communicated. However, since the oil pump body is composed of a mass body such as cast iron, vibration is attenuated by the mass effect. In addition, since a gap is provided between the outer periphery of the brake plate support portion and the inner periphery of the case, vibration is not directly transmitted from the brake plate support portion to the case. As a result, gear noise generated from the case can be reduced.

In claim 2, since the outer peripheral side of the brake plate is spline-fitted to the drum-like component, the meshing vibration (gear sound) of the pinion gear is transmitted to the drum-like component when the brake is engaged. Although the oil pump body is fixed to the case, a vibration isolating material is interposed between the oil pump body and the drum-shaped part, and the vibration transmitted to the oil pump body is effectively attenuated by this vibration isolating material. At the same time, it is also attenuated by the mass effect of the oil pump. Furthermore, since there is a gap between the drum-shaped component and the case, the vibration of the drum-shaped component is not directly transmitted to the case. As described above, the synergistic effect of the mass effect of the oil pump main body and the anti-vibration effect of the anti-vibration material suppresses the vibration transmitted to the case and reduces gear noise. Furthermore, there is an effect that the eccentricity of the brake plate can be absorbed by the deformation of the vibration isolator.
A known rubber can be used as the vibration isolator. The oil pump body and drum-like parts can be easily joined by rubber vulcanization.

According to a third aspect of the present invention, a hydraulic piston that presses one side surface of the brake plate and fastens the brake is disposed in the case, and a stopper portion that supports the opposite side surface of the brake plate against the pressing force of the hydraulic piston is provided as an oil pump. It is good to form integrally with a main body or a drum-shaped component.
Since one side of the brake plate is pushed by the hydraulic piston, a snap ring is generally attached to the groove of the transmission case to support the opposite side. However, since the portion where the pressure is applied to the brake plate and the groove in which the snap ring is fitted are offset in the radial direction, the snap ring is likely to be deformed such as torsion. Therefore, it is necessary to arrange a thick flange part inside the snap ring, and there is a problem that the space efficiency is poor.
On the other hand, if the axial end of the brake plate is supported by the oil pump body fixed to the transmission case or the stopper of the drum-shaped part, a snap ring and a thick flange part become unnecessary, Since the pressure of the hydraulic piston can be supported in the axial direction, there is an advantage that the brake plate is less deformed and the durability is improved.

In the present invention, the brake plate may be either a disk or a plate. When the outer peripheral side of the plate is splined to the stationary member and the inner peripheral side of the disc is splined to the rotating element, the plate corresponds to the brake plate.
The oil pump main body in the present invention is a stationary part excluding a rotating member (pump gear, rotor, etc.) of the oil pump, and may be either an oil pump body or an oil pump cover.
The brake of the present invention may be either a forward brake or a reverse brake. For example, in the case of a single pinion type planetary gear device, a forward brake is provided between the carrier and the case, and in the case of a double pinion type planetary gear device, a reverse brake is provided between the ring gear and the case.

As described above, in claim 1, even if the meshing vibration of the pinion gear is transmitted to the oil pump main body via the brake plate, the vibration is attenuated by the mass effect of the oil pump main body, and further, the vibration from the brake plate support portion to the case Is not transmitted directly, the vibration of the case can be suppressed and gear noise can be reduced.

Further, according to the second aspect, not only the vibration is attenuated by the mass effect of the oil pump main body, but is further attenuated by the vibration isolating effect of the vibration isolating material interposed between the oil pump main body and the drum-shaped member. Vibration can be suppressed and gear noise can be reduced more effectively.

Embodiments of the present invention will be described below with reference to examples.

1 to 3 show an example of a continuously variable transmission using a planetary gear device according to the present invention.
The continuously variable transmission of this embodiment is an FF horizontal type automobile transmission. As shown in FIG. 1, an input shaft 3 and an input shaft 3 driven by an engine output shaft 1 via a torque converter 2 are used. The forward / reverse switching mechanism 4 that transmits the rotation to the drive shaft 10 by switching between forward and reverse, the continuously variable transmission A comprising the drive pulley 11, the driven pulley 21, and the V belt 15 wound between both pulleys, and the driven shaft 20. A differential device 30 that transmits power to the output shaft 32 is provided. The input shaft 3 and the drive shaft 10 are arranged on the same axis, and the driven shaft 20 and the output shaft 32 of the differential device 30 are arranged parallel to the input shaft 3 and non-coaxially. Therefore, this continuously variable transmission has a three-axis configuration as a whole.
The V belt 15 used in this embodiment is a known metal belt composed of an endless tension band and a number of blocks supported by the tension band.

Each component constituting the continuously variable transmission is accommodated in a transmission case 5. An oil pump 6 is disposed between the torque converter 2 and the forward / reverse switching mechanism 4. As shown in FIG. 2, the oil pump 6 includes a pump body 7 fixed to the front side surface of the transmission case 5 by a bolt B1, and a pump cover 8 fixed to the rear side surface of the pump body 7 by a bolt B2. The pump gear 9 is accommodated between the pump body 7 and the pump cover 8. The pump body 7 and the pump cover 8 constituting the oil pump main body are formed of a mass body such as cast iron. The pump cover 8 is housed inside the case 5, but a predetermined gap δ is provided between the outer periphery of the pump cover 8 and the inner periphery of the case 5. The pump gear 9 is driven by the pump impeller 2 a of the torque converter 2. The turbine runner 2b of the torque converter 2 is connected to the input shaft 3, and the stator 2c is supported by the pump cover 8 via the one-way clutch 2d.

As shown in FIG. 1, the forward / reverse switching mechanism 4 includes a planetary gear device 40, a reverse brake 50, and a direct coupling clutch 51, and a sun gear 41 of the planetary gear device 40 is connected to an input shaft 3 that is an input rotation member. The ring gear 42 is connected to the drive shaft 10 which is an output rotating member. The planetary gear device 40 is a single pinion system, the reverse brake 50 is provided between the carrier 44 supporting the pinion gear 43 and the transmission case 5, and the direct clutch 51 is provided between the carrier 44 and the sun gear 41. . When the direct clutch 51 is released and the reverse brake 50 is engaged, the rotation of the input shaft 3 is reversed and decelerated and transmitted to the drive shaft 10. On the contrary, when the reverse brake 50 is released and the direct clutch 51 is engaged, the carrier 44 and the sun gear 41 of the planetary gear device 40 rotate together, so that the input shaft 3 and the drive shaft 10 are directly connected.
The specific structure of the forward / reverse switching mechanism 4 will be described later.

The drive pulley 11 of the continuously variable transmission A is a fixed sheave 11a formed integrally on a drive shaft (pulley shaft) 10 and a movable supported on the drive shaft 10 so as to be axially movable and integrally rotatable. A sheave 11b and a hydraulic servo 12 provided behind the movable sheave 11b are provided. A piston portion 12a extending to the back side is integrally formed on the outer peripheral portion of the movable sheave 11b, and the outer peripheral portion of the piston portion 12a is in sliding contact with the inner peripheral portion of the cylinder 12b fixed to the drive shaft 10. A hydraulic oil chamber 12c of the hydraulic servo 12 is formed between the movable sheave 11b and the cylinder 12b, and the shift control is performed by controlling the hydraulic pressure to the hydraulic oil chamber 12c.

The driven pulley 21 includes a fixed sheave 21a formed integrally on a driven shaft (pulley shaft) 20, a movable sheave 21b supported on the driven shaft 20 so as to be axially movable and integrally rotatable, and a movable sheave. And a hydraulic servo 22 provided behind 21b. A cylinder portion 22a extending to the back side is integrally formed on the outer peripheral portion of the movable sheave 21b, and a piston 22b fixed to the driven shaft 20 is in sliding contact with the inner peripheral portion of the cylinder portion 22a. A hydraulic oil chamber 22c of the hydraulic servo 22 is formed between the movable sheave 21b and the piston 22b. By controlling the hydraulic pressure of the hydraulic oil chamber 22c, a belt thrust necessary for torque transmission is given. Note that a spring 24 for applying an initial thrust is disposed in the hydraulic oil chamber 22c.

One end portion of the driven shaft 20 extends toward the engine side, and the output gear 27 is fixed to this one end portion. The output gear 27 meshes with the ring gear 31 of the differential device 30, and power is transmitted from the differential device 30 to the output shaft 32 extending left and right to drive the wheels.

In the continuously variable transmission configured as described above, at the time of forward movement, the reverse rotation brake 50 is engaged and the direct coupling clutch 51 is released, whereby the driving force input from the torque converter 2 is reversed and decelerated and transmitted to the driving pulley 11. The Then, the output shaft 32 is driven in the same direction as the engine rotation direction via the driven pulley 21 and the differential device 30.
On the other hand, during reverse travel, the direct clutch 51 is engaged and the reverse brake 50 is released, so that the input side (sun gear 41) and the output side (ring gear 42) of the planetary gear device 40 are directly connected. The drive force thus transmitted is transmitted to the drive pulley 11 as it is, and the output shaft 32 is driven in the direction opposite to the engine rotation direction via the driven pulley 21 and the differential device 30.
Thus, a compact continuously variable transmission can be realized with a three-axis configuration.

Here, the specific structure of the forward / reverse switching mechanism 4 will be described in detail with reference to FIGS.
The carrier 44 includes a disk-shaped carrier flange 45 and an annular carrier rim 46, and the inner diameter portion of the carrier flange 45 extends in the inner diameter direction between the sun gear 41 and the ring gear 42, and is rotatable about the input shaft 3. It is supported by. The carrier flange 45 is integrally formed with a plurality of (for example, six) columnar portions 45a protruding in the axial direction toward the carrier rim 46, and the pinion gear 43 is disposed in a space between the columnar portions 45a. The front end surface of the columnar portion 45a and the carrier rim 46 are metal-bonded by sintering, and the carrier flange 45 and the carrier rim 46 are integrally fixed. It may be fixed by welding, brazing, screwing or the like.

A pinion shaft 47 that supports the pinion gear 43 is supported between the carrier flange 45 and the carrier rim 46. A needle bearing 48 is disposed in the radial gap between the pinion gear 43 and the pinion shaft 47, and the pinion gear 43 is rotatable with respect to the pinion shaft 47.

The carrier rim 46 serves as both a brake hub of the reverse brake 50 and a clutch drum of the direct coupling clutch 51. That is, the carrier rim 46 is integrally formed with a cylindrical portion 46b that protrudes in the axial direction toward the front side (engine side), and an outer periphery of the clutch plate 51a of the direct coupling clutch 51 is formed on the inner peripheral portion of the cylindrical portion 46b. The diameter is splined. On the outer peripheral portion of the carrier rim 46, the inner diameter portion of the brake plate 50a of the reverse brake 50 is spline-fitted.

The piston 50b of the reverse brake 50 is accommodated in a concave hydraulic chamber 50c formed on the inner wall of the transmission case 5 as shown in FIG. 2, and the piston 50b is operated by the hydraulic pressure supplied to the hydraulic chamber 50c. One side of the brake plate 50a is pressed. As shown in FIG. 3, the outer peripheral claw portion 50a ₁ of the brake plate 50a is splined into the spline groove 8c between the comb-like brake plate support portions 8a integrally projecting backward from the pump cover 8 which is a stationary member. It is mated. Further, the outer peripheral claw portion 50a ₁ is also spline-fitted into a spline groove 5a formed in the inner peripheral surface of the transmission case 5 through the brake plate support portion 8a. The reason why the outer claw portion 50a ₁ of the brake plate 50a is spline-fitted in the spline groove 5a of the transmission case 5 in this manner is as follows. That is, in general assemble the pump cover 8 to the casing 5 after inserting the brake plate 50a to the casing 5 but, since the position of the outer peripheral pawl portion 50a ₁ of the brake plate 50a can not assemble the pump cover 8 is disjoint, the outer periphery It utilizes spline grooves 5a as a guide for aligning the position of the claw portion 50a _1. The clearance in the radial direction and the circumferential direction between the outer peripheral claw portion 50a ₁ and the spline groove 5a is set to be larger than the clearance between the outer peripheral claw portion 50a ₁ and the brake plate support portion 8a, and the outer peripheral claw portion 50a _{1 in the} assembled state. Is prevented from contacting the case 5. A gap δ is provided between the outer periphery of the pump cover 8 including the brake plate support portion 8a and the inner periphery of the case 5, and they are not in contact with each other. Further, the pump cover 8 is integrally formed with a stopper portion 8b that is a reaction force portion that supports the opposite side surface of the brake plate 50a pressed by the pressure of the piston 50b. The stopper portion 8b supports a substantially central portion in the radial direction of the brake plate 50a, and can support the pressure of the piston 50b so as to face each other in the axial direction.

As shown in FIG. 2, a cylindrical portion 41a serving as a clutch hub of the direct coupling clutch 51 is integrally projected on the front side (engine side) of the sun gear 41. The inner diameter portion of 51a is spline-fitted. A concave hydraulic chamber 51b is formed on the rear surface side of the pump cover 8, the piston 51c is operated by the hydraulic pressure supplied to the hydraulic chamber 51b, and the direct coupling clutch 51 is fastened. The piston 51c has a U-shaped cross section, and a thrust bearing 52 that allows relative rotation is attached to the side surface of the piston 51c that faces the clutch plate 51a. Therefore, the axial pressure of the piston 51c is effectively transmitted to the clutch plate 51a, and the piston 51c is prevented from rotating with the clutch plate 51a of the direct coupling clutch 51. Since the carrier rim 46 is disposed behind the clutch plate 51a, the opposite side surface of the clutch plate 51a pushed by the piston 51c can be supported by the side surface of the carrier rim 46. A part of the outer peripheral portion of the piston 51 c is engaged with the spline groove portion 8 c of the pump cover 8 and its rotation is restricted. The inner diameter portion of the bearing retainer 53 that supports the thrust bearing 52 extends toward the inner diameter side along the side surface of the piston 51c. One end side of the return spring 54 is supported on the pump cover 8 via a spring retainer 55, and the other end of the return spring 54 is in contact with the end surface of the piston 51c. As a result, the piston 51c is biased toward the hydraulic chamber 51b.

As described above, the brake plate support portion 8a in which the outer diameter portion of the brake plate 50a of the reverse brake 50 is spline-fitted is formed integrally with the pump cover 8 which is a stationary member. The pump cover 8 is attached to the pump body 7. Further, the pump body 7 is fixed to the case 5. The meshing vibration of the pinion gear 43 is transmitted to the pump cover 8 via the carrier rim 46 and the brake plate 50a. However, since the pump cover 8 and the pump body 7 are made of a mass body such as cast iron, vibration is caused by the mass effect. Is attenuated. In addition, since a gap δ is provided between the pump cover 8 and the case 5, vibration is not directly transmitted from the pump cover 8 to the case 5. As a result, gear noise generated from the case 5 can be effectively reduced.

In this embodiment, since the hydraulic piston 51c for fastening the direct coupling clutch 51 is disposed in the pump cover 8 which is a stationary member, it is necessary to provide a seal ring for preventing oil leakage in the supply oil path to the hydraulic piston 51c. The friction loss can be reduced. In addition, a complicatedly shaped clutch drum can be omitted, the structure can be simplified, and the processing cost can be reduced.

FIG. 4 shows a forward / reverse switching mechanism using a second embodiment of the planetary gear device according to the present invention. In FIG. 4, the same parts as those in FIG.
In the forward / reverse switching mechanism 4 ′, a drum-shaped member 61 is joined to the outer peripheral portion of the pump cover 8 via a rubber 60 that is a vibration isolator. In this example, the pump cover 8 and the drum-shaped member 61 are vulcanized and bonded via a rubber 60. A comb-like brake plate support portion 61a is integrally formed at the rear portion of the drum-shaped member 61, and the outer peripheral claw portion of the brake plate 50a is spline-fitted to the brake plate support portion 61a. The outer peripheral claw portion of the brake plate 50 a penetrates between the brake plate support portions 61 a and is fitted into the spline groove 5 a of the case 5. The drum-like member 61 is formed with a flange-like stopper portion 61b, and this stopper portion 61b supports the opposite side surface of the brake plate 50a against the pressing force of the piston 50b. The outer peripheral surface of the drum-shaped member 61 is not in contact with the inner peripheral surface of the case 5, and a predetermined gap is provided between them.

Also in this embodiment, transmission of gear vibration to the case 5 is suppressed by the mass effect of the pump cover 8 and the pump body 7, and at the same time, the prevention between the pump cover 8 and the drum-shaped part 61 is prevented. Gear vibration is effectively damped by the vibration rubber 60. Therefore, due to the synergistic effect of the mass effect of the oil pump main body and the anti-vibration effect of the anti-vibration rubber 60, vibration transmitted to the case 5 is greatly suppressed, and gear noise can be effectively reduced. Further, the elastic deformation of the vibration isolating rubber 60 has an effect of absorbing the eccentricity of the brake plate 50a.

In Figure 3, an example is shown in which the outer peripheral claw portion 50a ₁ is splined to the spline grooves 5a of the transmission case 5 penetrates between the brake plate supporting portion 8a of the brake plate 50a, limited to this structure is not.
FIG. 5A shows an example in which the spline groove is not formed on the inner peripheral surface of the transmission case 5 and the outer peripheral claw portion 50a ₁ is substantially the same height as the outer peripheral surface of the comb-like brake plate support portion 8a. FIG. 5B shows a structure in which a spline groove 8 c is formed on the inner peripheral surface of the pump cover 8 in place of the comb-like brake plate support portion. In any case, a gap δ is provided between the outer peripheral surface of the pump cover 8 and the inner peripheral surface of the case 5.
In this embodiment, it is necessary to align the position of the outer peripheral claw portion 50a ₁ of the brake plate 50a by some means at the time of assembly.

The present invention is not limited to the above embodiments.
In the above embodiment, the single-pinion type planetary gear device has been described, but the double-pinion type or any other type of planetary gear device can also be applied. That is, the present invention can be applied to any structure as long as the planetary gear device is housed in the case and one rotating element of the planetary gear device is configured to be fastened and released with respect to the stationary member via the brake device. Therefore, the present invention can be applied not only to continuously variable transmissions but also to general automatic transmissions.
The brake plate support portion can be provided not only on the pump cover but also on the pump body.
In the above embodiment, the pump cover 8 is fixed to the pump body 7 with bolts, and the pump body 7 is fixed to the case 5 with bolts. However, the pump body 7 is fixed to the pump cover 8 with bolts, and the pump cover 8 is You may fix to case 5 with a volt | bolt. However, if the pump cover 8 provided with the brake plate support portion 8a is fixed to the case 5 via the pump body 7 as in the embodiment, the mass effect for attenuating gear noise can be more effectively applied.

1 is a skeleton diagram of an example of a continuously variable transmission to which a planetary gear device according to the present invention is applied. FIG. 2 is a detailed cross-sectional view of a first embodiment of a planetary gear device applied to the continuously variable transmission of FIG. 1. FIG. 3 is a cross-sectional view showing an engagement relationship among a brake plate, a brake plate support portion, and a transmission case of FIG. It is a half sectional view of the second embodiment of the planetary gear device. It is sectional drawing which shows the other Example of the engagement relation of a brake plate, a brake plate support part, and a transmission case. It is sectional drawing of the forward / reverse switching mechanism of the conventional continuously variable transmission.

Explanation of symbols

3 Input shaft 4 Forward / reverse switching mechanism 5 Case 6 Oil pump 7 Pump body 8 Pump cover 8a Brake plate support 8b Stopper 40 Planetary gear unit 41 Sun gear 42 Ring gear 43 Pinion gear 44 Carrier 50 Reverse brake 50a Brake plate 50b Piston 51 Direct coupling clutch 60 Anti-vibration rubber 61 Drum-shaped member

Claims (3)

In a planetary gear device that is housed inside a case and configured so that one rotating element can be fastened and released via a brake to a stationary member,
The stationary member is an oil pump body fixed to the case;
The oil pump main body is integrally formed with a brake plate support portion that spline supports the outer periphery of the brake plate of the brake,
A planetary gear device, wherein a gap is provided between an outer periphery of the brake plate support portion and an inner periphery of the case. In a planetary gear device that is housed inside a case and configured so that one rotating element can be fastened and released via a brake to a stationary member,
The stationary member is a drum-like component that supports the outer peripheral side of the brake plate of the brake by spline,
The drum-shaped part is joined to the oil pump main body fixed to the case via a vibration isolator,
A planetary gear device, wherein a gap is provided between an outer periphery of the drum-shaped component and an inner periphery of the case. A hydraulic piston that presses one side of the brake plate to fasten the brake is disposed in the case,
The stopper part which supports the opposite side surface of the said brake plate with respect to the pressing force of the said hydraulic piston is integrally formed in the said oil pump main body or the said drum-shaped components, The Claim 1 or 2 characterized by the above-mentioned. Planetary gear device.

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