JPH03163244A - Automatic transmission - Google Patents

Abstract

PURPOSE:To obtain the sliding revolution, prevent the growth of abrasion and prolong the service life by using a member whose surface is boron-hardening- treated for thrust washers which supports both the edges of a pinion inside a carrier supporting part. CONSTITUTION:Pinions P1 and P2 having thrust washers 12a, 12b, 15a, and 15b at both the edges are installed on the pinion shafts 6 and 7 which are supported by a supporting part 2 which is erection-formed from the boss part 1 of the carrier CR 1 of a planetary gear unit 20. A member which is hardening- processed with the boron having high abrasion resistance is used for the surface of the washers 12a, 12b, 15a, and 15b. Accordingly, the smooth sliding revolution is obtained, and the superior abrasion resistance is obtained, and the growth of abrasion is prevented, and long service life is secured.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to an automatic transmission installed in an automobile, and particularly to an automatic transmission equipped with a gear unit having dual gears. relates to an automatic transmission having a thrust washer in a pinion support portion of a gear unit.

[Conventional technology]

Recently, the present applicant has published, for example, Japanese Patent Application Laid-Open No. 62-9354.
As shown in Publication No. 5, an automatic transmission equipped with a three-speed or four-speed forward automatic transmission mechanism consisting of a planetary gear unit that combines a single planetary gear and a dual planetary gear was devised.

The automatic transmission mechanism is constructed by integrally connecting the sun gear and carrier of both planetary gears, and uses the carrier as an output element, and rotates the input shaft through a single planetary gear ring gear (hereinafter referred to as a small ring gear).
At the same time, the ring gear of the dual planetary gear (hereinafter referred to as the large ring gear) is fixed to obtain the first speed, and the sun gear is fixed in the input state to the small ring gear to obtain the second speed. The gear unit rotates integrally to obtain three speeds, thereby forming an automatic transmission mechanism with three forward speeds.

Furthermore, a third clutch is attached that connects and disconnects the input wheel and the large ring gear, transmits the rotation of the input shaft to the large ring gear, and fixes the sun gear to obtain 4th speed.
It has an automatic speed change mechanism.

Generally, in an automatic transmission having an automatic transmission mechanism as described above, the pinion in the planetary gear unit is supported at its center by a pinion shaft provided in the carrier support part of the gear unit, and is supported by a twenty-one dollar bearing, and both ends are supported by thrust washers. This thrust washer consists of a washer member made of steel such as SPCC steel and a washer member made of phosphor bronze, with the steel washer member facing the pinion side (inside).
A washer member made of phosphor bronze is arranged on the supporting part side (outside). In other words, the pinion is made of a hard carburized steel material, while the carrier is a relatively soft material made of pressed material or low carbon steel. By providing a soft washer member made of phosphor bronze, the relative rotation of the two washer members is reduced, and wear of the carrier support portion and the phosphor bronze washer member itself is reduced.

[Problem to be solved by the invention]

However, in the structure of the thrust washer as described above, although the two washer members reduce the relative rotation, the phosphor bronze itself is soft, so when the pinion rotates at high speed with respect to the carrier support. However, there was a problem in that the washer member made of phosphor bronze wore out.

In particular, when applied to a 4-speed forward automatic transmission mechanism, the carrier rotates relatively during the 4th forward speed, which is used for a long time, and the pinion also rotates at high speed, causing rapid wear of the phosphor bronze washer member. Since it is unavoidable,
There was a desire for a thrust washer with sufficient durability to support the pinion.

Therefore, an object of the present invention is to improve the durability of the thrust washer by using a washer member with high wear resistance, thereby providing an automatic transmission that solves the above-mentioned problems. .

[Means to solve the problem]

The present invention has been made in view of the above-mentioned circumstances, and as shown, for example, with reference to FIG. A post part (1) of a carrier (CRI) is rotatably supported by a rotating member (5), and
The pinion shaft (6.7) has a support part (2) that is formed upright from the post part (1) and supports the pinion shaft (6.7), and the pinion shaft (6.7) has a pinion (P1 In an automatic transmission equipped with thrust washers (12a, 12b, 15a, 15b) supporting both ends of the thrust washers (12a.
12b. 15a. 15b) is characterized in that a washer member whose surface is subjected to boron hardening treatment is used.

And the thrust washers (12a, 12b,
1 5 a. 15 b) may include a washer member whose surface is subjected to boron hardening treatment on the carrier support portion (2) side and a steel washer member on the pinion (Pi, P2) side. .

Moreover, the thrust washer (1 2 a. 1 2
b, 1 5 a. 15b) may be a combination of two washer members whose surfaces are subjected to boron hardening treatment.

Alternatively, the thrust washers (12a, 12b,
1 5 a. 15 b) may be one in which the surface is secured by a washer member whose surface is hardened with boron, and the washer member is prevented from rotating with respect to the carrier support part (2>). .

[Effect]

In the automatic transmission having the above structure, the pinion (P
1. When the pinion (P2) rotates at high speed, the pinion (P1
．． P2) and thrust washer (12 a. 1 2
b. 1 5 a. 1 5 b) and between the thrust washers + (12a, 12b, 15a, 15b) and the carrier support part (2>), the relative rotation is at high speed, but the washer whose surface is subjected to boron hardening treatment Due to the low coefficient of friction of the component, the contact surfaces on both sides of the component slide extremely smoothly.Also, due to the high wear resistance, the smooth sliding is coupled with a reduction in the rate of surface wear.

In particular, in the case of thrust washers (12a, 12b, 15a, 15b) that are provided with a steel washer member on the inside, the relative rotation of the washer member whose surface is hardened with boron is reduced, resulting in wear on the surface. The speed is further reduced.

Furthermore, a thrust washer (l2 a, 1
2b, 15a, 15b), the wear rate of the washer member surface is further reduced.

In addition, thrust washers (12a, 12b, 15
a. 15b) and is prevented from rotating, rotation with the support part is prevented, and the washer member rotates smoothly in contact with only the end surface of the pinion (PI.P2).

〔Example〕

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

First, an outline of the automatic transmission A to which the present invention is applied will be explained with reference to FIG.
and a front axle shaft 23a, 23b, a torque converter 26 having a lock-up clutch 25 on the input shaft 3, and a four-speed forward automatic transmission mechanism 10.
An underdrive mechanism 27 is supported on the counter shaft 22, and a front axle shaft 23a is supported on the counter shaft 22.
, 23b, a front differential device 29 is supported.

The 4-speed automatic transmission mechanism 10 has a planetary gear unit 20 which is a combination of a single planetary gear 17 and a dual planetary gear 19, and the planetary gear unit 20 has a planetary gear unit 20 which is a combination of a single planetary gear l7 and a dual planetary gear 19. are integrally connected, and the pinion that meshes with Sangya S1 is a long pinion P.
1, the ring gear Rl (small ring gear) of the planetary gear 17 is connected to the ring gear Rl (small ring gear) via the first (forward) clutch C1, and The human power wheel 3 and the Sanghya S1 are connected to the second (
(reverse) clutch C2. Further, the Sangya S1 is directly connected and locked by the first brake B1, and its one-way rotation is locked by the second brake B2 via the first one-way clutch F1.

In addition, the ring gear R2 of the dual planetary gear l9 (
The large ring gear) is directly locked by a third brake B3, and one-way rotation is locked by a second one-way clutch F2.

The gear and rear CRI are connected to a counter drive gear 31 supported by a case bulkhead 40''.
The gear 31 becomes an output member of the four-speed automatic transmission mechanism 10.

Then, the above-mentioned clutches CI, C2 and brakes Bl, B
2. The one-way clutches Fl and F2 are the same as the 3-speed automatic transmission mechanism, but the 4-speed automatic transmission mechanism is the same as the 3-speed automatic transmission mechanism. A third clutch CO that connects R2, a fourth clutch C3 and a third one-way clutch FO interposed between the output side member of the clutch CO and the small ring gear R1.
is attached.

Further, the underdrive mechanism 27 has one single planetary gear 32, and a carrier CR3 and a sun gear S3 of the single planetary gear are connected via a fifth (direct) clutch C4. Also, Sanghya S
3 is directly locked by a fourth (underdrive) brake B4, and one-way rotation is locked by a fourth one-way clutch F3. The ring gear R3 is connected to a counter driven gear 33 which meshes with the counter drive gear 31 and becomes a manual member of the underdrive mechanism 27, and the carrier CR3 is connected to the counter shaft 22. Furthermore, a reduction gear 35 that serves as an output member of the underdrive mechanism 27 is fixed to the counter shaft 22.

The front differential device 29 also includes a differential carrier 36 and left and right side gears 37a. 37b, and a ring gear 39 is fixed to the differential carrier 36 which serves as a gear mount case. The ring gear 39 meshes with the reduction gear 35 to maintain the final reduction mechanism, and the left and right side gears 37a and 37b are connected to the left and right front axle shafts 23a and 37b, respectively. 23b.

Next, the 4-speed automatic transmission mechanism 10 in the automatic transmission A
The operation will be explained with reference to FIG.

The rotation of the engine crankshaft 2l is controlled by the torque converter 26.
or via the lock-up clutch 25 to the input shaft 3. In the first speed state in the D range, the first clutch C1 is in a connected state. In this state, the rotation of the human power shaft 3 is caused by the rotation of the first clutch C1.
, and in this state, the large ring gear R2 is transmitted to the second one-way clutch F2.
Since the rotation is prevented by , the common carrier CR1 is rotated at a significantly reduced speed in the forward direction while the sun gear S1 is idly rotated in the reverse direction, and the rotation is taken out from the counter drive gear 31.

Further, in the second speed state in the D range, the second brake B2 is operated in addition to the engagement of the first clutch C1. Then, the rotation of the sangya S1 is stopped by the operation of the first one-way clutch F1 based on the brake B2, and therefore, the rotation of the small ring gear R1 from the input shaft 3 causes the carrier CRI to rotate while causing the large ring gear R2 to idle in the forward direction. The rotation is decelerated in the positive direction, and this rotation is caused by the counter drive gear 1.
It is taken out as 2nd speed at 0. In addition, when shifting from l to 2, the second
The one-way clutch F2 is switched from the locked state to the overrun state, and shifts smoothly without causing a shift shock due to changing clutches.

In the third speed state in the D range, the third clutch C3 and the fourth clutch C4 are connected from the second speed state. Then, the information is transmitted from the input shaft 3 to the small ring gear Rl via the first clutch CI, and to the large ring gear R2 via the third clutch CO, and the propeller gear unit 19 rotates as a unit, resulting in direct coupling. The rotation is transmitted to the counter drive gear 31. Note that when shifting from 2 to 3, the first one-way clutch F1 is switched from a locked state to an open-balance state, and shifts smoothly without causing a shift E"J due to clutch change. In this case, the fourth clutch C3 is used together with the third clutch CO.
is connected, and the rotation of the input shaft 3 is also transmitted to the small ring gear Rl via a path via the third clutch CO1, the fourth clutch C3, and the third one-way clutch FO.

When upshifting from 3rd speed to 4th speed in the D range, first clutch C1 is released. In this state, rotation is exclusively transmitted to the small ring gear R1 through a path via the third clutch CO, fourth clutch C3, and third one-way clutch FO, and in this state, B1 is activated. Then,
Sangya S1 is also stopped against reverse rotation, and the rotation of large ring gear R2 transmitted from input shaft 3 via third clutch CO overruns one-way clutch FO, causing small ring gear R1 to idle at high speed. Career CR
It is taken out as an overdrive rotation from I. On this occasion,
Since the first clutch c1 is in the released state and the gears are changed under the action of the third one-way clutch FO, the gear shift is performed smoothly without causing any shift shock due to the clutch change.

Furthermore, in the engine brake operating state such as 3rd range, 2nd range, or 1st range, the third brake B3 operates in 1st gear to stop the large ring gear R2 against reverse rotation; At high speed, the first brake B1
is activated to stop Sangya S1 even in reverse rotation.

In the reverse range, the second clutch C
2 is connected, and the third brake B3 is activated.

In this state, the rotation of the input shaft 3 is transmitted to the sangya Sl via the second clutch C2, and in this state, the large ring gear R2 is fixed by the operation of the third brake B3, so the small ring gear R2 is fixed by the operation of the third brake B3. While the ring gear R1 is rotated in the opposite direction, the carrier CR1 is also rotated in the opposite direction, and the reversed rotation of the carrier is taken out by the counter drive gear 31.

On the other hand, the underdrive mechanism 27 is connected to the fourth brake B.
4 and (or) when the sangya S3 is in a stopped state due to the fourth one-way clutch F3, the rotation from the counter driven gear 33 is transferred from the ring gear R3 to the carrier CR3.
It is extracted as a deceleration (underdrive) rotation. Further, when the fourth brake B4 is released and the fifth clutch C4 is engaged, the carrier CR3 and the sangya S3
are integrated, and direct rotation is taken out to the counter shaft 22.

In the automatic transmission A, the four forward speeds of the four-speed automatic transmission mechanism 10 and the deceleration and direct connection of the underdrive mechanism 27 are appropriately combined to obtain a predetermined gear, and the rotation is controlled by the reduction gear 35 and the ring gear. 39 to the front differential device 29, and further to the left and right front axle shafts 23a, 23b. For example, the combination of the 4-speed automatic transmission mechanism 10 and the underdrive mechanism 27 is such that the underdrive mechanism 27 is in a deceleration state, the 4-speed automatic transmission mechanism 10 is operated to set the power mode, and the underdrive mechanism 27 is directly connected to the 4-speed Automatic transmission mechanism 1
The underdrive mechanism 27 may be set to an extra low or high setting to operate in special cases. It is conceivable to put the 4-speed automatic transmission mechanism 10 between 2nd and 3rd speeds to obtain 5th forward speed.

Next, an embodiment of the automatic transmission A described above will be described with reference to FIG.

The automatic transmission A has an integrated case consisting of a transaxle case 40, a transaxle housing 41, and a rear cover 42, and the case serves as a differential carrier for the input shaft 3, counter shaft 22, and front differential device 29. A ring gear mount case 36 is rotatably supported. A torque converter 26 having a lock-up clutch 25 and a four-speed automatic transmission mechanism 10 are disposed on the input shaft 3, and an underdrive mechanism 27 is disposed on the counter shaft 22. Further, a valve body 44 covered with a side force bar 48 is disposed in the transaxle case 40.

The 4-speed automatic transmission 10 includes a brake section 43, an output section 45, a planetary gear unit 20, and a clutch N47 arranged in this order from the engine crankshaft 21 toward the rear in the axial direction, and further includes a brake section 43 and a torque converter. An oil pump 49 is disposed between the input shaft 26 and the input shaft 3, and a hollow shaft 5 is rotatably supported by being fitted onto the input shaft 3.

The planetary gear unit 20 is composed of a single planetary gear 17 and a dual planetary gear 19 (see FIG. 2), and the single planetary gear 17 is composed of a sun gear S11J, a sun gear Rl-U, and a sun gear S11J formed in the hollow shaft 5. Carrier C supporting pinion P1 that matches these gears
The dual planetary gear 19 supports a sun gear S1 and a ring gear R2 formed on the hollow shaft 5, as well as a first pinion PI that meshes with the sun gear S1 and a second pinion P2 that meshes with the ring gear R2 so as to mesh with each other. It consists of carrier CRI. Both of these planetary gears 17 and 19 consist of a single gear with the same number of teeth formed on the hollow shaft 5, and the carrier cR1 is integrally constructed, and the pinion P
1 consists of an integrated long pinion.

The carrier CRI is, as detailed in Figure 1,
The post B1 has a post part 1, and the post B1 is provided with a support part 2 which rises in the radial direction from the end thereof and is integrally formed. Further, a pusher 9 is disposed between the inner circumferential surface of the post section 1 and the outer circumferential surface of the hollow shaft 5, and a post section 31a of a counter drive gear 31 is spline-coupled to the outer circumferential surface of the post section 1. At the same time, the ring gear R2 and the support member 50 of the outer race of the one-way clutch F2, which are arranged in parallel on the outer circumferential portion of the carrier CRI, are in contact with the force counter gear post portion 31a via the thrust bearing 60. On the other hand, the support part 2 has vinyl PI. The shafts 6.7 of P2 are fitted and fixed, and each of these shafts 6.7 has a 21 dollar bearing lla. llb
．． 13a and 13b, the pinion Pi. P2 is supported, and the pinions PI and P2 are each formed by a thrust washer l2a. whose surface is hardened with boron. 12b. Both ends are supported by 15a and 15b. In this embodiment, thrust washers 12a, 12b. 15a. As 15b, a thrust washer 12 is provided with a washer member whose surface is hardened with boron on the outside and a steel washer member on the inside.
a, 12b. 15a and 15b are used. These two washers have substantially the same shape, and the shapes are shown in FIGS. 5(a) and 5(b). Further, a thrust bearing 6l is in contact with the support portion 2 on the opposite side of the pinion shaft 6.7, and supports the support member 50 rotatably together with the thrust bearing 60.

Further, the bush 59 is provided with a hole 9a in the center thereof, and the hole 9a communicates with an oil hole 5a formed in the hollow shaft 5. Further, a groove 1a is formed on the inner circumferential surface of the post section 1 facing the bush L9, and the groove 1a communicates with the hole 9a of the push 9. Moreover, a large number of oil passages 2a are formed in a radial shape inside the support portion 2, and the base ends of the oil passages 2a communicate with the groove 1a. A portion of the large number of oil passages 2a communicates with an oil passage 6a formed in the shaft 6 supporting the first pinion, and the tip thereof is closed with a plug. The other oil passage 2a is an oil passage 7a formed in the shaft 7 supporting the second pinion.
The tip is closed with a stopper 2b.

In addition, oil passages 5a and 7 formed in these shafts 6.7
The tip of a is closed with plugs 6d and 7d, and a horizontal hole g formed in the shaft 6 and 7 is formed in the middle part.
h? ht = 1 chomatsu h 100 direct gogo phantom letter ηAh7
b is 21 dollar bearing lla. Ilb, 13a, 13
b and thrust washi+12a. 12b, 15a. 15
It is open to lubricate b.

As a result, an oil path is formed that forcibly lubricates the bearing and thrust washer from the oil hole 5b.

In addition, since the lubricating oil supplied from the oil hole 5b is guided to the groove 1a via the oil hole 9a, the lubricating oil is supplied to the post section 1 and the hollow shaft 5.
There will be no leakage between the two.

Further, in the brake part 43, a one-way clutch F1, a first brake B1 consisting of a multi-disc brake, and a second brake B2 consisting of a multi-disc brake are disposed in order from the inner diameter side to the outer diameter direction. ing. And the first
In the one-way clutch F1, the tip of the hollow shaft 5 is spline-engaged with the inner race, and a second brake hub extending radially outward is fixed to the outer race. Further, a first brake hub is fixed to the front side (engine side) of the inner race of the one-way clutch F1. On the other hand, oil a 'J + fA
n IJ "F II. -? If J -k"
'l L J-. - 4P t Jj s- -/
It consists of an oil pump assembly in which a J-bar is integrally fixed to the pump body with bolts across the pump plate. On the rear side of the oil bomb cover, a first brake hydraulic actuator 52 and a second brake hydraulic actuator 51 are disposed in order from the inner diameter side in an annular manner.

On the other hand, the output section 45 has a counter drive gear 31 located approximately in the center of the 4-speed automatic transmission mechanism 10, and the counter drive gear 31 is connected to the axle case 40.
It is rotatably supported via a double tapered bearing 53 by a partition wall 40'' shaped like
is connected to. Furthermore, the outer race of the bearing 53 is splined and fitted to the inner circumferential surface of the case partition wall 40', and a second one-way clutch F2 is attached to the outer circumferential surface of the race extension.

The outer race of the second one-way clutch F2 is the ring gear R of the dual gear gear 19.
2, and the ring gear R2 is connected to the counter gap post section and the carrier C through a thrust bearing.
It is supported by a support plate that is supported between it and the RI. Further, a third brake B3 is interposed between the outer periphery of the ring gear R2 and the axle case 40, and a cylinder is formed on one side wall surface of the partition wall 40°, and the cylinder has a hydraulic pressure composed of a piston. Acticoator 65
is arranged so as to be sandwiched between the second one-way clutch F2 and the second one-way clutch F2.

The clutch section 47 includes a first (forward) clutch C1 and a second (reverse) clutch C2, and is located at the rear end of the 4-speed automatic transmission mechanism 10 and is housed in the transaxle force bar 42. has been done. Further, a sleeve portion 3a is fixed to the rear end of the input shaft 3 so as to fit over the center post portion 42a of the cover 42, and a clutch drum 67 is integrally connected to the sleeve portion 3a. Further, a movable member 69 is fitted to the clutch drum 67 by a spline so as to be slidable only in the axial direction, and a piston member 70 is fitted to the movable member 69 in an oil-tight manner. Moreover, the movable member 69 is the clutch drum 6
7. An oil chamber is formed between the cylinder and the inner circumferential surface of the first cylinder.
A hydraulic actuator 71 for the clutch Cl is constructed.

On the other hand, the piston member 70 forms an oil chamber between it and a cylinder formed from the inner peripheral surface of the movable member 69, thereby forming a hydraulic actuator 72 for the second clutch C2. Further, a spring 73 is compressed between the piston member 70 and a spring receiving member 7l fixed to the sleeve portion 3a with a snap ring, and the spring 73 is connected to the piston members of both hydraulic actuators 71 and 72. It constitutes a return spring common to 69.70. Further, the first clutch C1 is interposed between a spline formed on the inner peripheral surface of the outer diameter portion of the clutch drum 67 and a spline formed on the axially extending portion surface of the ring gear R1. 2
The clutch C2 is connected between a spline formed on the inner peripheral surface of the outer diameter part of the movable member 69 and a spline formed on the inner peripheral surface of the outer diameter part of the movable member 69. Intervening.

The four-speed automatic transmission mechanism 10 includes the following devices in addition to the common parts with the three-speed automatic transmission mechanism described above. That is, a sleeve member 75 is fitted into the annular post portion 42b of the rear cover 42, a flange member 79 is fixed to the sleeve member 75, and the third clutch CO
The cylinder of the hydraulic actuator 80 is used for this purpose.

A piston 77 is fitted in the cylinder in an oil-tight manner, and a comb-like slit is formed on the outer circumference of the flange member 79, and the outer friction for the third clutch CO is passed through the slit. A separator plate, a separator plate, and a packing plate are arranged. Further, a hub is fixed to the stepped portion of the clutch drum 67, and a clutch plate that engages with the hub and constitutes an internal friction plate is disposed, and the clutch plate and the separator plate control the hydraulic actuator. A third clutch CO is provided adjacent to the motor 8-0.

-Ko Ryoun I-}#Rusbu16j@97 has one single planetary gear 32 as shown in Issasa 9 darkness. Further, a counter driven gear 33 is rotatably supported on the counter shaft 22 via a bearing 103, and a reduction gear 35 is fixed on the shaft 22. The ring gear R3 of the branet gear 32 is connected to the counter driven gear 33, and the pinion P
The carrier CR3 supporting the counter shaft 22 is integrally formed with the counter shaft 22 bulging in the outer diameter direction. Furthermore, Sanghya S
3 is mounted on a hub 105 rotatably supported on a shaft 22, and a drum 106 is fixed to the outer diameter of the hub.
A fourth brake B4, which is a band brake, is engaged on its outer peripheral surface.

Further, a fifth clutch C4 is interposed between the inner peripheral surface of the drum 106 and a hub fixed to the carrier CR3, and a piston is fitted into the hub 105 adjacent to the clutch C4. This constitutes a hydraulic actuator 107 for clutch C4. Furthermore, a fourth one-way clutch F3 is interposed between the extension of the hub 105 and the case 40.

Further, the front differential device 29 has a ring gear mount case 36 that serves as a differential carrier, and the case 36 is rotatably supported by the housing 41 and the case 40 via bearings. Further, a large-diameter ring gear 39 that meshes with the reduction gear 35 is fixed on the mount case 36, and a pinion gear 111 is rotatably supported by a pinion shaft 110 inside the ring gear 39. Left and right side gears 37a and 37b that mesh with 111 are rotatably supported. The side gears 37a and 37b have left and right front axle shafts 23a. 23b are respectively fitted and connected.

Since the present embodiment has the above-described configuration, when the automatic transmission A is driven, the rotation appropriately shifted by the 4-speed automatic transmission mechanism 10 is taken out from the carrier CRI and transferred from the counter drive gear 31 to the counter driven gear 33. The signal is transmitted to the underdrive mechanism section 27 via.

At this time, the carrier CR1 rotates according to each gear stage, and the pinion Pi. P2 also rotates.

And pinion Pi. Thrust washers supporting both ends of P2 +12a. 12b, 15a, 15b are constructed by disposing a washer member whose surface is hardened with boron on the outside and a steel washer member on the inside,
The relative rotation of these two washer members is reduced, and the outer washer member, whose surface is hardened with boron, smoothly slides and rotates.

In particular, when the 4-speed automatic transmission mechanism 10 is in 4th gear, the ring gear R1 of the single planetary gear 17 idles at high speed, and the ring gear R1 of the dual planetary gear 19
The input rotation is transmitted to the pinion P1 and the second pinion P2, and therefore the first pinion P1 and the second pinion P2 rotate at high speed, but even during such high speed rotation, the outer washer member whose surface is hardened with boron slides smoothly. At the same time, there is almost no wear.

sshi+12a. 12b, 15a, and 15b were constructed with two pieces, a steel washer member (inner side) and a washer member (outer side) whose surface was hardened with boron, but as another example,
Both sheets may be used as washer members whose surfaces are subjected to boron hardening treatment.

As yet another embodiment, the thrust washer 12a. 12b,
15a and 15b may be used interchangeably. and,
In this case, since relative rotation cannot be reduced as in the case of using two washer members, the washer member is prevented from rotating relative to the support part 2 in order to prevent wear of the support part 2. It is preferable. For example, the hole in the washer member is shown in FIG. 6(a). The pinion shaft 6.7 has the shape shown in (b), and the washer portion of the pinion shaft 6.7 has the same shape as the hole in the washer member to prevent rotation. Or the hole in the washer member! Figure 7(a). The shape is provided with a notch as shown in (c), and a protrusion that fits this notch is provided on the support portion 2 side to prevent rotation.

A powder or granular hardening agent made of a mixture of charcoal, carborundum, etc. is prepared, then a steel punched into the shape of a thrust washer is embedded in the hardening agent in a heat-resistant steel container, and the container is covered with a lid. Place it in a heating furnace and heat it to 800-1000℃.
This is done by heating for a time corresponding to the hardening treatment to a predetermined depth and then cooling.

〔Effect of the invention〕

As explained above, according to the present invention, the thrust washer that supports both ends of the pinion inside the carrier support section has a
Since we used a washer member whose surface was hardened with boron, even when the pinion rotates at high speed relative to its support, this washer member slides and rotates extremely smoothly, reducing its own wear. This can be prevented, and the progression of wear of the support portion can also be prevented.

In particular, when the carrier rotates at high speed (for example, when driving a Saiichi bar), the pinion also rotates at high speed, and the relative rotation between the supports at both ends becomes extremely fast, and the pinion remains at this high speed for a long time. As the relative rotation of speeds continues, wear of the rotating contact surface tends to progress, but the washer member whose surface is hardened with boron can prevent wear as much as possible even under such conditions. At the same time, it is possible to prevent the progress of wear of the support portion, and as a result, it is possible to extend the life of the thrust washer.

Further, by providing the steel washer members in parallel inside, the relative rotation between the two washer members can be reduced, and furthermore, it is possible to prevent the washer member whose surface is subjected to boron hardening treatment from being worn out.

Further, by using two washer members whose surfaces are subjected to boron hardening treatment, both of the washer members are further reduced in wear, and the thrust washer can withstand even longer use.

Further, by constructing the thrust washer with a single washer member whose surface is hardened with boron, the number of parts can be reduced.

[Brief explanation of the drawing]

FIG. 1 is a sectional view showing the main parts of an automatic transmission according to the present invention, FIG. 2 is a schematic diagram of the automatic transmission according to the present invention, FIG. 3 is a diagram showing its operation, and FIG. 4 is a diagram showing the invention. 5(a) is a front view showing the washer member, FIG. 5(6) is a longitudinal sectional view of FIG. 5(a), and FIG. Front view showing another example of the washer member, No. 6
Figure (B) is a longitudinal sectional view of Figure 6(a), Figure 7(a) is a front view showing still another embodiment of the washer member, and Figure 7(B) is a longitudinal sectional view of Figure 7(a). FIG. 1... Carrier post part, 2... Carrier support part, 5
... Rotating member (hollow shaft), 6... Inner pinion shaft, 7... Outer pinion shaft, 12a. 12b
．． 15a, 15b... Thrust washer, 20...
Brane gear unit, A... automatic transmission, CRI
...Carrier, P1...Inside (first) pinion, P
2...Outside (second) pinion

Claims (1)

[Scope of Claims] 1. A planetary gear unit, wherein a post section of a carrier of the gear unit is rotatably supported by a rotating member, and the carrier is formed rising from the post section and supports a pinion shaft. In the automatic transmission, the pinion shaft is provided with a thrust washer that supports both ends of the pinion, and the thrust washer is a washer member whose surface is hardened with boron. automatic transmission. 2. The thrust washer includes a washer member whose surface is hardened with boron on the carrier support side and a steel washer member on the pinion side. 1. The automatic transmission described in 1. 3. The automatic transmission according to claim 1, wherein the thrust washer includes two washer members whose surfaces are hardened with boron. 4. A claim characterized in that the thrust washer comprises a single washer member whose surface is hardened with boron, and the washer member is prevented from rotating relative to the carrier support portion. Item 1
Automatic transmission as described.