JPH06201022A - Vehicle transmission - Google Patents

Abstract

PURPOSE:To conduct oil feeding without oil leakage to attain appropriate lubrication in a planetary gear unit consisting of two kinds of planetary gears by constituting in a carrier, in a non-penetrating state in the radial direction, a radial directional hole for pinion shaft locking tool insertion and a lubrication hole crossing the pinion shaft hole. CONSTITUTION:A four-speed automatic transmission contains a four-speed transmission gear mechanism, which is provided with a planetary gear unit composed of combination of a single planetary gear with a dual planetary gear, and sun gears S1, S2 thereof are integratedly formed. A carrier CR is common for pinions P1, P'1 meshed with the sun gears S1, S2. In this transmission, a lubricating oil passage (shaft hole) 21 is formed in the axis of a pinion shaft 20 connected to the carrier CR and in this oil passage 21 radial directional holes 22-24 are arranged. The shaft hole 21 is connected to a radial directional hole 26 in the carrier CR, which is connected to radial directional holes 27, 28 formed in a sun gear sleeve 19 and an input shaft 15.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission for a vehicle, and more particularly to a lubricating structure for a washer between a pinion and a carrier of a planetary gear used in the transmission for a vehicle.

[0002]

2. Description of the Related Art Conventionally, lubrication of a pinion and a washer between gears used in a planetary gear of an automatic transmission for a vehicle, and lubrication of a needle bearing between a pinion and a pinion shaft are provided by centrifugal force from the shaft center of an input shaft. The oil is supplied to the outer side in the radial direction of the carrier by the centrifugal force accompanying the rotation of the carrier through a radial hole formed in the carrier, and this hydraulic pressure is applied to the shaft of the pinion shaft arranged in the direction perpendicular to the carrier. It was supplied to the washer and the needle bearing through an oil hole formed in the core and further through a radial hole formed in a pinion shaft connected to the oil hole. At this time, the radial hole formed in the carrier is usually penetrated for ease of processing, and the through hole is usually formed by intersecting the shaft hole formed in the pinion shaft. It was And, even if it is a through hole, the supply of oil to the shaft hole of the pinion shaft is not insufficient.

[0003]

However, when the rotation speed of the carrier is high, that is, when the rotation speed of the carrier is usually the engine rotation speed ratio of 1.0 at the maximum speed stage, it becomes higher than that. Due to the centrifugal force generated by the rotation of the carrier, it leaks through the clearance between the pinion shaft stopper and the through hole that is inserted into the through hole from the outside in the radial direction. The lubricating oil is not always supplied to.

In particular, when the number of pinions is increased as in the double planetary gear, a further amount of lubricating oil is required.
This is because the number of needle bearings and washers that require lubrication increases.

Therefore, an object of the present invention is to provide a lubricating oil supply structure for supplying sufficient lubricating oil into the pinion shaft through radial holes formed in the carrier.

Further, in a planetary gear unit consisting of a single planetary gear and a dual planetary gear, since the number of pinion gears increases, more and more lubricating oil is required, and it is an object to provide a structure capable of supplying sufficient lubricating oil even in such a case. And

[0007]

According to the present invention, an input shaft 15 for transmitting engine driving force, a planetary gear unit 12 connected to the input shaft, and a plurality of shifts are connected between elements of the planetary gear unit. In a transmission including a plurality of frictional engaging elements and an output shaft 13 connected to one element of the planetary gear unit, the planetary gear unit 12 includes the sun gears S ₁ and S ₂ and a pinion P that meshes with the sun gears. ₁ ,
P ₁ 'and P ₂ and the pinion shaft 2 supporting the pinion
The pinion shaft 20 has a center hole in its axial center and radial holes 22, 23 which are connected to the planetary gears 10, 11 which are composed of a carrier CR which is connected to 0 and a ring gear which meshes with the pinion. , 24, and the carrier CR has a first radial hole 2 into which a locking tool 26 for locking the pinion shaft 20 is inserted.
6'is formed from the outside in the radial direction toward the center, and is formed from the inside in the radial direction toward the outside in the radial direction to form a second radial hole 26 "communicating with the central hole 21 of the pinion shaft. The radial hole 26 'and the second radial hole 26 "are formed in a non-penetrating state.

Further, the planetary gear unit 12 has a structure including a double planetary gear 11 composed of a combination of a plurality of planetary pinions P ₁ 'and P ₂ .

Also, the planetary gear unit 12
Is provided adjacent to the single planetary gear 10 and the single planetary gear, the sun gears S ₁ and S ₂ are connected to each other, the carrier CR is connected to each other, and the carrier is connected via the double pistons P ₁ ′ and P _2. A dual planetary gear 11 including a ring gear R ₂ and the carrier CR connected to the output shaft 13,
The ring gear R _{1 of the} single planetary gear has a structure connected to the input shaft 15 via a clutch means.

[0010]

According to the present invention, the carrier CR of the planetary gear is provided with a second radial hole 26 "as a lubrication hole which crosses the axial hole of the pinion shaft from the radially inner side toward the radially outer side for pinion locking. Since it is configured to be in a non-penetrating state with the first radial hole 26 ', for example, even when the rotation speed of the carrier is higher than the rotation speed of the engine, centrifugal force causes oil to leak to the outside in the radial direction. Without
Washers 40, 41, 42 and needle bearing 4
It is possible to properly lubricate 8, 48 ', 49, etc.

Further, even when the pinion has a high rotational speed in a device having an appropriate gear ratio by the structure including the sun gear S ₁ having different numbers of teeth of the double planetary gear unit,
Appropriate lubrication can be provided to improve the durability of the washers 40, 41, 42.

[0012]

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

FIG. 1 is a sectional view showing an essential part of the invention relating to a transmission of the present invention, FIG. 2 is a side sectional view of a carrier showing a lubricating structure of the present invention, and FIG. 3 is a sectional view of a washer. 4 is a full sectional view of the transmission according to the present invention, FIG. 5 is a diagram showing a skeleton of the transmission of the present invention, and FIG. 6 is an operation table of the transmission of the present invention.

First, the structure of the transmission will be described with reference to FIG.

The four-speed automatic transmission A to which the present invention is applied is
It has a torque converter 50 via a lockup clutch L / C, a fourth speed transmission gear mechanism 1, a reduction mechanism 51 and a differential device 52.

The four-speed transmission gear mechanism 1 has a planetary gear unit 12 formed by combining a single planetary gear 10 and a dual planetary gear 11, and the sun gears S ₁ and S _{2 of the} gear unit 12 are integrally formed. The sun gear S is formed.

Further, the sun gear S₁, S₂Mesh with Pini
ON P₁, P₁’Has a common carrier CR,
Also, the ring of the pinion and the dual planetary gear 11
Gear (hereinafter referred to as "large ring gear") R ₂Mesh with
Pinion P₂The carrier CR that supports the
ing. Then, from the output member of the torque converter 50
The extending input shaft 15 is the first clutch C.₁Through ream
The second clutch C that is connected to the connecting member 16₂
Is connected to the sun gear S via.

Further, the ring gear of the connecting member 16 and the single planetary gear 10 (hereinafter referred to as "small ring gear").
The third clutch C ₃ and the second one-way clutch F ₀ are interposed between R ₁ and R 4, and the fourth clutch C ₀ is interposed between the connecting member 16 and the large ring gear R _2. There is.

The sun gear S is constructed so that it can be locked by a _first brake B ₁ which is a band brake, and a second brake is provided between the large ring gear R ₂ and the case 17. B ₂ and the first one-way clutch F ₁ are interposed. Further, the carrier CR is an output gear 1 which is an output shaft located substantially in the center of the transmission gear mechanism 1.
It is linked to 3.

The speed reducing mechanism 51 has a counter shaft 54 rotatably supported by the case,
A large gear 53 and a small gear 55 that are constantly meshed with the output gear 13 are fixed to the shaft 54. In addition, the differential device 52 includes a differential pinion 5 that meshes with each other.
6 and the left and right side pinions 57a and 57b are fixed to the left and right front axles 59a and 59b, respectively.
The diff pinion 56 is supported by a diff carrier 60 that is rotatably supported by the case, and a ring gear 61 that is constantly meshed with the small gear 55 is attached to the diff carrier 60.

Next, the lubrication structure of the essential part of the present invention will be described with reference to FIG.

The planetary gear unit 12 has a single planetary gear 10 and a dual planetary gear 11, and the carrier CR and the sun gear S are integrally connected.

The sun gear S extends in the axial direction, and the input shaft 1
5 has a sleeve 19 supported on it. Carrier CR
Comprises a sleeve 18 extending axially and supported on a sleeve 19.

The carrier CR has a pinion shaft 20.
Are connected in the vertical direction, and an oil passage 21 for lubrication is formed in the shaft center of the shaft 20. In the oil passage 21, radial holes 22, 23, 24 are arranged so that lubricating oil is supplied to the teeth and washers of each pinion. Shaft 2
A plug 25 is provided at one end of the shaft hole 21 formed in the hole 0, and the oil passage is closed. The shaft hole 21 is connected to a radial hole 26 in the carrier, and the hole 26 is connected to a radial hole 27 formed in the sun gear sleeve 19 and a radial hole 28 formed in the input shaft 15. The radial hole 26 formed in the carrier and the radial hole 27 formed in the sun gear sleeve are connected via a groove 29 formed inside the carrier sleeve 18 in the radial direction.

Bushings 30 and 31 are arranged between the carrier sleeve 18 and the sun gear sleeve 19, and the grooves 2
A bush 30 is disposed so as to abut against the shaft 9, and a hole is formed in the bush 30 so that oil communicates with the groove 29 through the radial hole formed in the sun gear sleeve. The carrier is formed with two radial holes, and the first radial hole 26 'is formed from the outer side in the radial direction toward the center, and the pinion shaft locking tool 26 is inserted thereinto, and the second radial hole 26' is formed. Radial hole 26 "
The first and second radial holes 26 ', 26 "are formed in a non-penetrating state. The closed oil passage is formed only by communicating with the shaft hole 21 formed in the pinion shaft 20. There is.

Of the carrier CR and the dual planetary gear
Pinion P ₁Between the bronze washer 32 and
Steel washers 33 are provided side by side.

Lubricating oil is supplied to the washers 32 and 33 through a radial hole 34 of the input shaft 15 and a radial hole 35 formed in the sun gear sleeve 19.

Single planetary gear pinion P₁When
Dual planetary gear pinion P ₁Between the two
Steel washers 36, 37 on one side and a bron between them
A washer 38 is provided for the sun gear S.₁And S₂of
The radial direction of the input shaft through the radial hole 39 formed between
Lubricating oil is supplied from the hole 34.

Carrier CR and single planetary gear 1
Steel washers 40 and 41 on both sides and a bronze washer 42 are disposed between the pinions P ₁ of 0, and the lubricating oil is positively applied through the radial holes 24 formed in the pinion shaft. Is being supplied. Further, the lubricating oil supplied to the bearing 44 through the radial hole 43 formed in the input shaft can also be supplied to the washers 32, 38, 42. The lubricating structure of the carrier will be described with reference to FIG.

Next, the structure of the washer in the present invention will be described with reference to FIG.

The washers 36, 37, 40, 41 are steel washers, and the pinion shaft 20 (FIG. 1) is passed through the circular center hole 45.

The washer 42 is a bronze washer, and the central hole 46 has a circular hole 42 through which the pinion shaft 20 (FIG. 1) penetrates, and a central hole 46 is 45 with respect to the vertical and horizontal axes.
Four oil reservoir chambers 47a, 47b at intervals of °,
47c and 47d are formed.

As a result, in the three-phase combination of the washers 36, 37, 38 and the three-phase combination of the washers 40, 41, 42, the window 47 of the bronze washer in the central portion is used.
An oil sump is formed in a to 47d, and the washer is sufficiently lubricated.

Next, with reference to FIG. 5, the operation at each shift speed will be described with reference to the operation table of the transmission of the present invention.

At the time of parking and neutral, the third
All brakes and clutches are released except the clutch C ₃ of.

In reverse, when the vehicle speed is lower than a predetermined value, the C ₂ clutch and the B ₂ brake are engaged, and when the vehicle speed is higher than the predetermined value, only the C ₂ clutch is engaged.

In the D range, only the C ₁ clutch is engaged at the 1st speed. Moreover, the first and second one-way clutches F ₁ and F ₀ are engaged, and the rotation of the input shaft 15 is
The first clutch C ₁ and the second one-way clutch F ₀
The rotation of the large ring gear R ₂ is transmitted to the small ring gear R ₁ via the first one-way clutch F _{1 in} this state, so that the carrier CR is widened while idling the sun gear S. It is decelerated and the decelerated rotation is taken out from the output gear 13. Then, the rotation of the output gear 13 is reduced by the reduction mechanism 51, and the differential device 52 further causes the left and right accelerator shafts 59a, 59a.
b.

Further, in the second speed state, the band of the first brake B ₁ is tightened. The rotation of the input gear 15 is the first
Via the clutch C ₁ and the second one-way clutch F ₀ of the transmitted to the small ring gear R ₁ and, since the first sun gear S by the brake B ₁ is being locked rotation of the small ring gear R ₁ is a large ring gear R _It is taken out from the carrier CR as a second speed rotation while spinning 2.

In the 1-2 shift, the first one-way clutch F ₁ is prevented from overrunning to prevent the occurrence of shift shock due to the grip change.

Further, during the 2-3 shift, the timing for engaging the fourth clutch C ₀ and releasing the first brake B ₁ is properly performed.

In the third speed state where the third clutch C ₃ and the fourth clutch C ₀ are engaged in addition to the _first clutch C ₁ and the first brake B ₁ is released, Axis 15
Is transmitted to the small ring gear R ₁ via the second one-way clutch F ₀ and the third clutch C ₃ and is transmitted to the large ring gear R 2 via the fourth clutch C ₀ , and the planetary gear unit 12 is The integrated rotation which is integrated is taken out from the carrier CR to the output gear 13.

At this time, the fourth clutch C ₀ and the first brake B ₁ are replaced by another clutch. However, as described above, the proper timing is taken and the shift through the other shift stages is blocked so that the shift is performed. There is no shock.

Next, in the fourth speed state, the first clutch C ₁ and the fourth clutch C ₀ are in the engaged state, and
The first brake B ₁ is switched to the locked state, and
In the fourth speed state in which the third clutch C ₃ is switched to the disengaged state, the rotation of the input shaft 15 is caused by the rotation of the fourth clutch C 3.
_{Since it} is transmitted to the large ring gear R ₂ via ₀ and the sun gear S is locked by the first brake B ₁ , the rotation of the large ring gear R ₂ causes the carrier CR to rotate at high speed while idling the ring gear R _1. It rotates and this rotation is transmitted to the output gear 13.

At this time, the first brake B₁Locking
With this, the third clutch C3 is released, but the third clutch C3 is released.
Clutch C₃Second one-wake even if the car is released early
Latch F ₀The 3rd speed state is maintained by the
First brake B₁By controlling the locking of the
Occurrence of shift shock due to grip change is prevented.

On the other hand, the time of 4-3 speed downshift, the first brake B ₁ is being released, the third clutch C ₃ is engaged, this time, the first brake B ₁ By controlling the release, the second one-way clutch F
Shifting from ₀ overrun to locking enables smooth shifts.

In the case of downshifting to the 3-2nd speed, the fourth
Of the clutch C ₀ is delayed with respect to the engagement of the first brake B ₁ , the fourth clutch C ₀ and the first brake B ₁ are both released, and the gear shifts through the first speed state, that is, 3- The shift operation such as the 1-2 speed is prevented.

The lubrication structure of the pinion shaft of the present invention will be described below.

As described above, in the fourth speed state, the pinion P
The diameter of ₁ is small and the relative rotational speed between the pinion P ₁ and the carrier CR increases.

For example, in the present embodiment, in the fourth speed, the rotation speed ratio of the carrier CR is 1.
361, the rotation speed ratio of the single planetary gear pinion P ₁ is 2.501, and the rotation speed ratio of the dual planetary small pinion P ₂ and large pinion P ₁ 'is 1.863, respectively.
It becomes 1.264. Therefore, pinion P ₁ and carrier C
Washers or needle bearings 48, 4 with R
8 ', 49 requires sufficient lubrication. Lubricating oil to the shaft center of the input shaft 15 passes through the radial hole 28 and the radial hole 27 of the sleeve 19 which is stationary at the 4th speed through the gap between the input shaft 15 and the sun gear sleeve 19. It is stored in the groove 29 formed in the carrier sleeve 18 through the hole formed in the bearing 30. Then, the rotation of the carrier CR causes the centrifugal force to supply oil to the radially outer side through the second radial hole 26 ″ of the carrier.
At this time, since the second radial hole 26 ″ is formed in a non-penetrating state in the first radial hole 26 ′ into which the locking tool 26 of the pinion shaft is inserted, oil leakage does not occur and the pinion does not occur. The radial hole 2 through the axis 21 of the shaft 20
Needle bearings 48,4 supplied to 2,23,24
8'and washers 40, 41, 42 are properly lubricated.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a main part showing a lubrication structure of a pinion according to the main part of the present invention.

FIG. 2 is a sectional view of a carrier showing a lubricating structure of the present invention.

FIG. 3 is a sectional view of a washer.

FIG. 4 is a sectional view of a transmission according to the present invention.

FIG. 5 is a skeleton diagram of the transmission of the present invention.

FIG. 6 is an operation table of the transmission of the present invention.

[Explanation of symbols]

10 Single planetary gear 11 Dual planetary gear (double planetary gear) 12 Planetary gear unit 13 Output shaft 15 Input shaft 20 Pinion shaft 21 Pinion shaft shaft hole 22, 23, 24 Pinion shaft radial hole 26 Locking device 26 'First radial direction hole 26 "second radial bore CR carrier _{P 1, P 1 ', P} 2 pinion shaft R _1, R ₂ ring gear S _1, S ₂ sun

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Kazuhisa Ozaki, 10 Takane, Fujii-cho, Anjo-shi, Aichi Aisin AW Co., Ltd.・ AW Co., Ltd.

Claims (3)

[Claims] 1. An input shaft for transmitting engine driving force, a planetary gear unit connected to the input shaft,
In a transmission comprising a plurality of friction engagement elements connected between elements of the planetary gear unit to achieve a plurality of shifts, and an output shaft connected to one element of the planetary gear unit, wherein the planetary gear unit is a sun gear, A planetary gear including a pinion that meshes with the sun gear, a carrier that is connected to the pinion shaft that supports the pinion, and a ring gear that meshes with the pinion is provided, and the pinion shaft has a central hole in its axis. The carrier has a radial hole, the carrier has a first radial hole into which a locking tool for locking the pinion shaft is inserted, and the first radial hole is formed from a radially outer side toward a center, and A second radial hole communicating with the central hole of the pinion shaft from the inside toward the outside in the radial direction, Serial vehicle transmission system, characterized in that said first radial bore second radial bore formed in the non-penetrating state. 2. The vehicle transmission according to claim 1, wherein the planetary gear unit includes a double planetary gear including a combination of a plurality of planetary pinions. 3. The planetary gear unit comprises a single planetary gear and a ring gear that is provided adjacent to the single planetary gear, has sun gears connected to each other, and carriers connected to each other, and is connected to the carrier via a double pinion. 2. A transmission according to claim 1, wherein the transmission is composed of a dual planetary gear, the carrier is connected to the output shaft, and the ring gear of the single planetary gear is connected to the input shaft via a control means. apparatus.