JP3036911B2 - Automatic transmission forced lubrication system - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automatic transmission having a planetary gear having a carrier connected to a shaft member so as to be relatively non-rotatable, wherein lubricating oil supplied from the shaft member is formed on the carrier. The present invention relates to a forced lubrication device that supplies oil from oil holes to a support surface of each pinion. More specifically, lubricating oil that supplies and distributes lubricating oil from a lubricating oil supply hole formed in a shaft member to a plurality of lubricating oil holes formed in a carrier plate. It relates to a dispensing device.

[0002]

2. Related Art Conventionally, as a lubricating device for a planetary pinion supporting surface, an oil reservoir plate is fixed to a side surface of a carrier plate and formed on an output shaft as proposed in, for example, Japanese Patent Application Laid-Open No. 61-48643. The lubricating oil from the lubricating oil supply hole is received by the oil reservoir plate based on centrifugal force, and the lubricating oil of the oil reservoir is guided to the pinion support surface.

In recent years, however, it has been necessary to supply a larger amount of lubricating oil to the pinion support surface with the increase in engine speed and output. However, the supply of lubricating oil through the oil reservoir described above has been difficult. It is difficult to sufficiently supply the lubricating oil, and there is a demand for a forced lubricating device that forcibly supplies the lubricating oil to each pinion support surface.

[0004]

However, in general, a forced lubricating device for a carrier that supplies lubricating oil to each pinion support surface has a shaft 5 formed on a shaft 5 as shown in FIGS. 4 (a) and 4 (b). A plurality of lubricating oil holes 31 formed in the carrier plate 21 are provided facing one radial direction supply hole 30a communicating with the direction lubrication supply hole 30. For example, as shown in FIG. 4A, when the carrier supports four pinions, four lubricating oil holes 31a, 31b, 31c, 3
When the carrier supports five pinions as shown in FIG. 4B, five lubricating oil holes 31e and 3e are formed.
If, 31g, 31h and 31i are formed.

For this reason, the amount of lubricating oil distributed and supplied to each lubricating oil hole 31 from one supply hole 30a differs.
Specifically, a lubricating oil hole 31a or 3 close to the supply hole 30a
1e is supplied with a large amount of lubricating oil, and an intermediate lubricating oil hole 31
An intermediate amount of lubricating oil is supplied to b, 31c or 31f, 31g, and only a small amount of lubricating oil is supplied to lubricating oil holes 31d or 31h, 31i far from the supply hole 31a. In particular, in the front planetary gear unit in which the carrier 21 always rotates integrally with the shaft 5, the supply amount to each of the lubricating oil holes 31 described above is fixed, and the unevenness of the lubricating oil supply amount is conspicuous. .

Accordingly, even if the total amount of the lubricating oil sent from the supply hole 31a is sufficient, the lubricating oil holes 3
Insufficient lubricating oil supply to 1d, 31h, 31i
There is a possibility that a problem may occur in the needle portion of the planetary pinion communicating with the lubricating oil hole.

[0007] Therefore, the present invention accumulates the lubricating oil from the lubricating oil supply hole into the oil sump and guides the lubricating oil overflowing from the lubricating oil hole to the lubricating oil hole to evenly distribute the lubricating oil to the plurality of lubricating oil holes. It is an object of the present invention to provide a forced lubricating device for an automatic transmission that distributes and supplies, and thus solves the above-mentioned problems.

[0008]

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned circumstances, and provides an automatic transmission comprising a planetary gear unit having a carrier connected to a shaft member so as to be relatively non-rotatable. A plurality of lubricating oil supply holes for forced lubrication formed in the shaft member, and a plurality of lubricating oil supply holes larger than the number of lubricating oil supply holes, each communicating with a support surface of each pinion formed in the carrier and rotatably supported by the carrier. A lubricating oil hole, an annular concave groove formed on the inner peripheral surface of the boss portion of the carrier, facing the lubricating oil supply hole opened on the outer peripheral surface of the shaft member, and a bottom surface of the concave groove. The bottom of the concave groove located radially outward from the openings of the plurality of open lubricating oil holes is formed, and the bottom is closed to collect lubricating oil based on centrifugal force and to overflow the lubricating oil. The lubricating oil hole Characterized by comprising and an oil reservoir leading to the mouth.

[0009]

According to the above construction, the lubricating oil from the lubricating oil supply hole of the shaft member is supplied to the concave groove on the inner peripheral surface of the boss portion of the carrier, and the lubricating oil is stored in the oil reservoir by centrifugal force based on the rotation of the carrier. Can be Then, the lubricating oil overflowing from the oil reservoir is guided to each lubricating oil hole, and the lubricating oil is uniformly supplied from the lubricating oil holes to the respective pinion support surfaces.

[0010]

As described above, according to the present invention,
The lubricating oil supplied from the lubricating oil supply hole is temporarily stored in the oil sump, and the lubricating oil overflowing from the lubricating oil supply hole is led to each lubricating oil hole. Lubricating oil can be supplied to the lubricating oil holes almost uniformly. Thereby, the shaft member having the lubricating oil supply hole and the carrier having the plurality of lubricating oil holes are always rotated integrally, and while having a very simple configuration, the plurality of pinion support surfaces are formed. All can be reliably lubricated, and the reliability of the automatic transmission can be improved.

[0011]

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

First, an automatic transmission 1 equipped with a front planetary gear unit 11 to which the present invention is applied will be described.
The outline of the automatic transmission 1 will be described with reference to FIG.
It has an OD (overdrive) input shaft 2, an input shaft 3, and an output shaft 5 arranged concentrically. On the OD input shaft 2, a torque converter 7 having a lock-up clutch 6 and an OD planetary gear unit 9 is disposed, while a main transmission unit 13 including a front planetary gear unit 11 and a rear planetary gear unit 12 is disposed on the output shaft 5. The three planetary gear units 9, 11, and 12 are all housed inside a transmission case 15.

The OD planetary gear unit 9 has a sun gear 16 fitted on the OD input shaft 2 and a carrier 17 directly connected to the OD input shaft 2.
A pinion 19 is meshed with the pinion 6. A ring gear 20 that is directly connected to the input shaft 3 of the main transmission unit 13 is meshed with the pinion 19. An OD direct clutch C0 and a one-way clutch F0 are interposed between the sun gear 16 and the carrier 17, and an OD brake B0 is interposed between the sun gear 16 and the transmission case 15.

The front planetary gear unit 11
A carrier 21 directly connected to the output shaft 5, a pinion 22 axially mounted on the carrier 21, a ring gear 23 meshing with the pinion 22, a front sun gear 25a meshing with the pinion 22;
Is formed at the front end and a sun gear 25 is formed at the rear end to form a rear sun gear 25b that meshes with the pinion 26 of the rear planetary gear unit 12. The sun gear 25 has a first coast brake B1 interposed between the transmission gear 15 and the sun gear 25.
And a direct clutch C2 is interposed therebetween.
Further, a forward clutch C1 is interposed between the ring gear 23 and the input shaft 3.

The rear planetary gear unit 12 has a ring gear 27 directly connected to the output shaft 5, a pinion 26 meshing with the ring gear 27, and a carrier 29 supporting the pinion 26, and a rear sun gear 25 meshing with the pinion 26.
b is formed at the front end and the rear end of the sun gear 25 together with the front sun gear 25a of the front planetary gear unit 11. The sun gear 25 is rotatably fitted to the output shaft 5, and a brake B2 is interposed between the sun gear 25 and the transmission case 15 via a one-way clutch F1. A brake B3 and a one-way clutch F2 are interposed between the carrier 29 and the transmission case 15 in parallel.

Next, the operation of the automatic transmission 1 will be described with reference to FIGS. Each clutch C0, C1, C2 of the automatic transmission 1, each brake B0, B1, B2, B
3 and the one-way clutches F0, F1, F2 are controlled as shown in the operation table of FIG. 3 at each shift speed at each of the positions P, R, N, D, 3, L. Note that in the figure, each clutch C0, C1, C
2. the engagement state of each brake B0, B1, B2, B3;
The locked state of each one-way clutch F0, F1, F2 is indicated by a circle, while the released state of the former and the free state of the latter are indicated by a cross. However, the ◎ marks of the one-way clutches F1 and F2 indicate
It shows that each one-way clutch F1, F2 is in a free state.

First, at the first speed in the D range or the third range, the OD direct clutch C0, the one-way clutches F0 and F2, and the forward clutch C1 are engaged, and the others are in the released state. Therefore, the auxiliary transmission unit 10
The OD planetary gear unit 9 is integrally connected directly via the OD direct clutch C0 and the one-way clutch F0, and the right rotation of the OD input shaft 2 is directly transmitted to the input shaft 3 of the main transmission unit 13. .
In the main transmission unit 13, the rotation of the input shaft 3 is transmitted to the ring gear 23 of the front planetary gear unit 11 via the forward clutch C1, and
2, while being transmitted to the output shaft 5 integrated with the pinion 22 and applying a leftward revolving force to the pinion 26 of the rear planetary gear unit 12 via the sun gear 25.
This revolution is prevented by the one-way clutch F2, and the pinion 26 rotates and transmits power to a ring gear 27 integrated with the output shaft 5. That is, the main transmission unit 13 is in the first speed state, and together with the direct connection state of the subtransmission unit 10,
The automatic transmission 1 as a whole is in the first speed state. At this time, when transmitting the rotational torque to the output shaft 5, the main transmission unit 13 transmits the rotational torque to the output shaft 5 via the front planetary gear unit 11 and the rear planetary gear unit 12.
, And the load received by each gear is distributed accordingly.

At the 2nd speed in the D range, the OD brake B0, the one-way clutch F2 and the forward clutch C1 are engaged, and the others are in the released state. Accordingly, in the subtransmission unit 10, the sun gear 16 is locked by the OD brake B0, the pinion 19 rotates and revolves to transmit power to the ring gear 20, and the speed is increased (OD) to the input shaft 3 of the main transmission unit 13. Transmit rotation. Also,
The main transmission unit 13 is the same as the previous first speed state, so that the first speed of the main transmission unit 13 and the speed increase of the auxiliary transmission unit 10 are combined to bring the entire automatic transmission 1 into the second speed state.

At the 3rd speed in the D range, the OD direct clutch C0, the one-way clutch F0, the forward clutch C1, the one-way clutch F1 and the brake B2 are engaged, and the others are in the released state. Therefore, the auxiliary transmission unit 10 is in the direct connection state described above, and the rotation of the OD input shaft 2 is transmitted to the input shaft 3 of the main transmission unit 13 as it is. The main transmission unit 13 transmits the rotation of the input shaft 3 to the ring gear 23 of the front planetary gear unit 11 via the clutch C1 and applies a leftward rotational force to the sun gear 25 via the pinion 22. The rotation in this direction is prevented by the one-way clutch F1 associated with the engagement of the brake B2, so that the pinion 22 revolves while rotating, and the second speed rotation is transmitted to the output shaft 5 via only the front planetary gear unit 11. You. As a result, the automatic transmission 1 as a whole has the third speed, due to the direct connection state of the subtransmission unit 10 and the second speed state of the main transmission unit 13.

At the 4th speed in the D range, the OD direct clutch C0, the one-way clutch F0, the forward clutch C1, the direct clutch C2 and the brake B2 are engaged, and the others are in the released state. Accordingly, the auxiliary transmission unit 10 is in the directly connected state described above, and the main transmission unit 13 is integrated with the front planetary gear unit 11 by the engagement of the clutches C1 and C2, and the rotation of the input shaft 3 remains unchanged as the output shaft. 5 is transmitted. As a result, the direct connection of the sub transmission unit 10 and the main transmission unit 1
In combination with the third speed, the fourth speed can be obtained in which the OD input shaft 2, the input shaft 3, and the output shaft 5 rotate integrally as a whole of the automatic transmission 1.

At the 5th speed in the D range, the OD brake B0, the forward clutch C1, the direct clutch C2 and the brake B2 are engaged, and the others are in the released state. Therefore, the auxiliary transmission unit 10 operates at the speed increase (O
D) state, and the main transmission unit 13 is also in the above-mentioned third speed state. Together with these two transmission units 10, 13, the fifth speed can be obtained as a whole of the automatic transmission 1.

In the R range, the OD direct clutch C0, the one-way clutch F0, the direct clutch C2 and the brake B3 are engaged, and the others are in the released state. Accordingly, the auxiliary transmission unit 10 is in a directly connected state, and the main transmission unit 13 is configured such that the rotation of the input shaft 3
2 directly to the sun gear 25 and the brake B
3, the pinion 2 of the rear planetary gear unit 12
6 is locked, the rotation of the sun gear 25 is transmitted to the ring gear 27 as the left rotation through the rotation of the pinion 26, and the output shaft 5 is reversed.

At the 3rd speed in the 3rd range or the L range, the first coast brake B1 is engaged in the 3rd speed in the D range described above, so that the rotation of the sun gear 25 is blocked in both directions. Engine braking becomes possible.

At the 1st speed in the L range, the brake B3 is engaged in the 1st speed in the D range. Therefore, the revolution of the rear pinion 26 is prevented in both directions, and engine braking is enabled.

As described above, when the main transmission unit 13 is in the first or second speed, the pinion 22 is rotated by the ring gear 23 in addition to the revolving motion of the carrier 21, and rotates relative to the carrier 21. Become. And
In particular, the speed increase by the auxiliary transmission unit 10 is added to this,
When the automatic transmission 1 is in the second speed as a whole, the relative rotation of the pinion 22 is increased, and it is necessary to increase the amount of lubricating oil supplied to the pinion 22. Further, in the front planetary gear unit 11, the carrier 21 is fixed to the output shaft 5 by a spline (5e; described later), and therefore, a lubricating oil supply hole (30a; described later) and a lubricating oil hole (31 ...; described later). Is fixed, and the lubricating oil amount to the lubricating oil hole far from the supply hole tends to be insufficient.

Next, the front planetary gear unit 11, which is a main part of the present invention, will be described in detail with reference to FIG.

The front planetary gear unit 11
The output shaft 5 is disposed around the output shaft 5 as a whole.
Are provided with lubricating oil supply holes 30 formed in the axial direction, and supply holes 30a, 30b, 30 formed in the radial direction from the supply holes 30.
and c form a lubricating oil supply path. The radial supply holes 30a, 30b, and 30c are formed on different planes in the axial direction, and supply lubricating oil to different lubricating parts.

A sun gear 25 is rotatably fitted to the rear side (the right side in FIG. 1) of the outer periphery of the output shaft 5. The sun gear 25 has inner and outer teeth 25a. And an oil passage 25e that communicates with the oil passage. Also, the tooth portion 25a
A drum member 32 is engaged with a rear end of the drum member 32. The drum member is connected to a direct clutch C2 at a front side thereof, and the rotation of the input shaft 3 causes the drum member 32 to rotate by engaging and disengaging the clutch C2. The sun gear 25 is connected to and disconnected from the sun gear 25. Further, when the drum member 32 is fixed by the first coast brake B1, the sun gear 25 is thereby locked.

On the outer peripheral surface between the lubricating oil supply holes 30b and 30c of the output shaft 5, splines 5e and 5e are formed on the front side and the rear side of the supply hole 30a therebetween.
A boss 21a of one plate 21 'of the carrier 21 is engaged with e. The boss portion 21a is formed to be long in the front-back direction, and the supply hole 30a of the output shaft 5 is formed in the middle in the axial direction.
Lubrication oil holes 31 opening toward the carrier plate 2
1 'is formed in the radial direction. The lubricating oil hole 31 further penetrates the pin 33 fixed to the carrier plate 21 ′ in the axial direction, and further penetrates in the radial direction to open toward the inner periphery of the pinion 22. Note that five (or four) pinions 22 are arranged at equal intervals in the circumferential direction of the carrier 21, and therefore, the lubricating oil holes 31 communicating with these pinions 22 are also arranged at equal intervals in the circumferential direction. 5 (or 4)
(See FIGS. 4A and 4B). A predetermined portion of the lubricating oil hole 31 is closed by a plug 35, and a joint portion of the output shaft 5 with the supply hole 30a is kept oil-tight by spline coupling before and after the same. The lubricating oil supplied through the pinion 2
2 is effectively supplied to the supporting surface. The pinion 22 is rotatably supported on the outer periphery of the pin 33 via a needle bearing 36, meshes with the teeth 25 a of the sun gear 25 on the inner diameter side, and engages with the inner peripheral surface of the ring gear 23 on the outer diameter side. Of the teeth 23b. In addition, washers 37 are arranged on the front end face and the rear end face of the pinion 22.

The ring gear 23 has a hub portion 39 formed on the inner diameter side, and the inner periphery of the hub portion 39 is formed on the carrier plate 2.
1 'is supported via bearings on the outer peripheral surface 21h of the boss portion 21a extending forward of the boss portion 21'.
Is entirely rotatably supported. A thrust bearing 4 is provided between the front surface of the ring gear 23 and the input shaft 3 and between the rear surface and the carrier plate 21 '.
0 is interposed. Further, a forward clutch C1 is interposed between the ring gear 23 and the flange member 3a integral with the input shaft 3, and this is connected to an actuator 41.
, The rotation of the input shaft 3 is connected to and disconnected from the ring gear 23. However, when the vehicle is moving forward, the forward clutch C1 is always engaged, whereby the ring gear 23 is constantly rotating.

An annular concave groove 42 is formed on the inner peripheral surface of the boss 21a of the carrier plate 21 'so as to face the lubricating oil supply hole 30a. The concave groove 42 has a bottom surface formed of an inclined surface 42a, and the inclined surface 42a
The plurality of lubricating oil holes 31 are opened at an intermediate position of
From there these oil holes extend in the radial direction. Therefore,
A portion deeper than the opening 31 ′ of the lubricating oil hole 31 of the concave groove,
That is, the closed bottom portion of the concave groove forms an oil reservoir A for storing the lubricating oil supplied from the supply hole 30a based on the rotation of the carrier plate 21 '. , Are substantially equally guided to the lubricating oil holes 31.

Next, regarding the operation of the above-described embodiment,
This will be described with reference to FIGS.

The carrier 21 of the front planetary gear unit 11 always rotates integrally with the output shaft 5, so that the positional relationship between the lubricating oil supply holes 30a and the lubricating oil holes 31 is kept constant. Therefore, without the forced lubrication device for the automatic transmission according to the present invention, as described above, the supply hole 30a
The supply amount of the lubricating oil to each of the lubricating oil holes 31 becomes uneven, and for example, from the fourth speed or the fifth speed, the kick down is performed.
At the third speed or the second speed, the pinion 22 rotates rapidly, but the lubricating oil holes 31 with a small supply amount described above (31d,
31h, 31i; see FIG. 4) may cause a problem due to poor lubrication in the pinion. In particular, when the auxiliary transmission unit 10 is in the overspeed (OD) state, the main transmission unit 13 is in the first speed state, and the automatic transmission 1 is kicked down to the second speed as a whole, the input shaft 3 rotates at an increased speed and the forward clutch The ring gear 23 also rotates at an increased speed via C1, while the sun gear 25 rotates in the opposite direction to the ring gear 23 based on the release of the direct clutch C2, whereby the pinion 22 rotates at high speed, that is, the pinion 22 In contrast, a large relative rotation occurs.

Even in such a case, in the present invention, the lubricating oil supplied from the lubricating oil supply hole 30a is guided to the annular groove 42, and the rotation of the carrier 21 causes the inclined surface 42a to rotate. It is stored in oil sump A consisting of the deep part,
The overflow from there is almost uniformly supplied to the lubricating oil holes 31. Thereby, even if the supply hole 30a and the lubricating oil hole 31 are always in a fixed positional relationship, substantially equal lubricating oil is distributed to each pinion 22, and all the pinions are reliably lubricated. Even if the pinion 22 rotates on its own, no problem occurs. Then, the lubricating oil forcibly supplied to the supply hole 30 of the output shaft 5 by a hydraulic device (not shown) does not leak out from the supply hole 30a.
Are supplied to the lubricating oil holes 31 of the carrier plate 21 ', and are further forcibly supplied to the support surface of each pinion 22, that is, the needle bearing 36. As a result, a sufficient amount of lubricating oil can be supplied to the bearings 36 supporting the respective pinions 22 substantially uniformly.

Although the above-described embodiment has been described with respect to an example in which the present invention is applied to the front planetary gear unit 11, the present invention is not limited to this and can be similarly applied to other planetary gear units.

Further, the oil reservoir A is not limited to be formed by the inclined surface formed on the bottom surface of the concave groove 42, but may be formed by another shape such as an arc surface.

[Brief description of the drawings]

FIG. 1 is a sectional view of a front planetary gear unit showing an embodiment of the present invention.

FIG. 2 is a schematic diagram of an automatic transmission to which the present invention can be applied.

FIG. 3 is a view showing the operation of the automatic transmission.

FIGS. 4 (a) and (b) are cross-sectional views showing distribution of lubricating oil by a device already proposed by the present applicant.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Automatic transmission 5 Shaft member (output shaft) 11 Front planetary gear unit 21 Carrier 21a Boss 21 'Carrier plate 22 Pinion 30, 30a Lubricating oil supply hole 31 Lubricating oil hole 31' Opening 42 Annular concave groove 42a Bottom surface (inclined) Surface) A oil sump

──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Yoshinori Shibayama 10 Takane, Fujii-machi, Anjo, Aichi Prefecture Inside Aisin AW Co., Ltd. (72) Yoshikazu Sakaguchi 10 Takane, Fujii-machi, Anjo, Aichi Prefecture Aishi (72) Inventor Yasuo Hojo 1 Toyota Town, Toyota City, Aichi Prefecture Inside Toyota Motor Corporation (72) Inventor Yutaka Taga 1 Toyota Town, Toyota City, Aichi Prefecture Inside Toyota Motor Corporation (56) References JP-A-61-41042 (JP, A) JP-A-2-17846 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16H 57/00-57 / 04

Claims (1)

(57) [Claims] 1. An automatic transmission comprising a planetary gear unit having a carrier connected to a shaft member so as to be relatively non-rotatable, wherein a lubricating oil supply hole for forced lubrication formed in the shaft member, and formed in the carrier. A plurality of lubricating oil holes, each of which is larger than the lubricating oil supply hole, respectively communicating with a supporting surface of each pinion rotatably supported by the carrier, and an outer peripheral surface of the shaft member on an inner peripheral surface of a boss portion of the carrier. An annular groove formed to face the lubricating oil supply hole that is open on the surface; and a radially outer side than the openings of the plurality of lubricating oil holes that open on the bottom surface of the groove. An oil sump formed at the bottom of the concave groove, the bottom being closed and the lubricating oil being accumulated based on centrifugal force and leading the overflowing lubricating oil to the opening of the lubricating oil hole. Automatic shifting characterized by Of forced lubrication system.