JP2844039B2 - Transmission for vehicles - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicular transmission and, more particularly, to an oil discharge structure for preventing oil agitation of an automatic transmission having a planetary gear.

[0002]

2. Description of the Related Art Conventionally, lubricating oil for a planetary gear used in a vehicle transmission is supplied as lubricating oil to, for example, a brake disposed radially outside of a ring gear through lubrication of a pinion, and the lubricating oil in the planetary gear is It also served the function of discharge.

[0003]

However, there has been a demand for a transmission that can be configured to be as compact as possible in the axial and radial directions and that can control multiple stages in a flexible manner. When a compact arrangement structure or the like is required, oil agitating action occurs from the radially inner side of the ring gear, which may cause a problem such as wear of each member due to heat generation.

Accordingly, an object of the present invention is to provide a compact transmission and a vehicle transmission capable of preventing oil agitation.

[0005]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides an input shaft for transmitting engine driving force, a planetary gear unit connected to the input shaft,
A vehicle transmission comprising: a plurality of frictional 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. A first clutch means connected between the ring gear and the input shaft, and a hub of the first clutch is disposed radially inward of the ring gear, and a connection control portion of the hub and the ring gear is provided. Has a structure in which radial holes for oil discharge are arranged.

Further, the planetary gear unit is provided with a single planetary gear, a first planetary gear, a first planetary gear, and a first planetary gear connected to each other from a sun gear, a carrier connected to each other, and connected to the carrier via a double pinion. The carrier is connected to the output shaft, the second ring gear of the single planetary gear is connected to the input shaft via a second clutch means, and the first clutch means Has a structure in which the hub is disposed radially outside the second ring gear.

[0007] Further, a first brake is disposed radially outside the first ring gear, and a predetermined gap is formed between the first clutch and the first brake. The ring gear has a structure in which a radial hole is formed, and oil flows toward the case through the hole.

Further, a one-way clutch is provided at an end of the first ring gear opposite to the hub, and a ring gear flange is provided between the one-way clutch and the planetary gear unit for connecting a spline to the first ring gear. It has an installed structure.

Further, a first bearing is provided between the flange and the dual planetary gear, and a second bearing is provided between the flange and a case to which an inner race of the one-way clutch is connected. It has a structure.

[0010]

According to the present invention, lubricating oil is supplied to the space formed between the clutch hub and the ring gear disposed radially inside the ring gear in order to achieve a compact structure. Since the oil discharging hole is formed in the vicinity, the oil stirred by the rotating member is discharged through the hole, and the discharged oil is collected along the case, whereby the stirring between the planetary gear units can be prevented. .

Further, the planetary gear unit has a combined structure of a single planetary gear and a dual planetary gear, and the first clutch means is arranged radially outside the second ring gear of the single planetary, so that the structure can be made more compact. At the same time, stirring can be prevented by oil discharge regardless of the presence of the rotating member.

Further, oil is discharged through a gap between a brake disposed radially outside the first ring gear and the first clutch, so that agitation after oil discharge does not occur. Oil is discharged along. Since the one-way clutch and the ring gear flange are disposed at one end of the first ring gear, oil can be properly discharged even in a state where a closed space is formed in the planetary gear unit.
Further, the durability of the bearings disposed on both sides of the ring gear flange is improved, and the effect of discharging the oil for lubricating the bearing is produced.

[0013]

Embodiments of the present invention will be described below with reference to the drawings. 1 is a cross-sectional view of a main part showing a lubrication structure of a pinion relating to a main part of the present invention, FIG. 2 is a cross-sectional view taken along the line AA of FIG. FIG. 4 is a sectional view of the washer. FIG. 5 is a full sectional view of the transmission according to the present invention, and FIG.
FIG. 7 is a diagram showing a skeleton of the transmission of the present invention, and FIG. 7 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 includes a torque converter 50 via a lock-up clutch L / C,
It has a four-speed transmission gear mechanism 1, a reduction mechanism 51, and a differential device 52.

The four-speed transmission gear mechanism 1 is a single planetar
The gear 10 and the dual planetary gear 11
Having a planetary gear unit 12 formed
And the sun gear S of the gear unit 12₁, S_TwoEach other
The sun gear S is integrally formed. Change
And sun gear S₁, S_TwoMesh with Pinion P₁,
P₁’Has a common carrier CR,
And the ring gear of the dual planetary gear 11
"Large ring gear") R _TwoPinion P meshing with
_TwoAre also integrally formed. So
And extends from the output member of the torque converter 50
The input shaft 15 is the first clutch C₁Via the connecting member 16
And the second clutch C_TwoThrough sa
Gear S. In addition, single with connecting member 16
The ring gear of the planetary gear 10 (hereinafter referred to as “small ring gear”
R)₁Between the third clutch C_ThreeAnd the second
One-way clutch F₀Is interposed, and the connecting part
Material 16 and large ring gear R_TwoBetween the fourth clutch C₀
Is interposed.

The sun gear S is configured to be locked by a _first brake B ₁ comprising 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 is interposed. Further, the carrier CR is an output gear 1 which is an output shaft located substantially at the center of the transmission gear mechanism 1.
3

The speed reduction mechanism 51 has a counter shaft 54 rotatably supported by a case. The shaft 54 has a large gear 53 and a small gear 55 which are always meshed with the output gear 13. Fixed. In the differential device 52, a differential pinion 56 and left and right side pinions 57a, 57b meshing with each other are fixed to left and right front axles 59a, 59b, respectively. The differential pinion 56 is supported by a differential carrier 60 that is rotatably supported by the case, and a ring gear 61 that is always meshed with the small gear 55 is attached to the differential carrier 60.

Next, the lubricating structure of the main 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 thereon. Carrier CR
Comprises a sleeve 18 extending in the axial direction and supported on a sleeve 19.

A pinion shaft 20 is vertically connected to the carrier CR, and an oil passage 21 for lubrication is formed at the axis of the shaft 20. In the oil passage 21, radial holes 22, 23, and 24 are provided so that lubricating oil is supplied to the teeth and washers of each pinion. Shaft 20
A plug 25 is provided at one end of the shaft hole 21 formed therein, 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 in the carrier sleeve 18 in the radial direction.

Bushes 30, 31 are provided between the carrier sleeve 18 and the sun gear sleeve 19, and grooves 29 are provided.
A bush 30 is provided so as to abut on the bush 30, and a hole is formed in the bush 30 to allow oil to communicate with the groove 29 from a radial hole formed in the sun gear sleeve. Two radial holes are formed in the carrier, and a first radial hole 26 ′ is formed from the outside in the radial direction toward the center. Hole 26 "is the first
And the second radial holes 26 ′, 26 ″ are formed in a non-penetrating state. The second radial holes 26 ′, 26 ″ merely communicate with a shaft hole formed in the pinion shaft to constitute a closed oil passage.

The carrier CR and the dual planetary gear
Pinion P ₁’Between the bronze washer 32
Steel washers 33 are provided side by side. Wa
The washer 32, 33 has a radial hole 34 of the input shaft 15 and a support.
Through a radial hole 35 formed in the gear sleeve 19
Lubricating oil is being supplied. Single planetary gear
Nion P₁And dual planetary gear pinion P ₁’
Steel washers 36, 37 on both sides
A bronze washer 38 is provided between the sun gear S
₁And S_TwoThrough the radial hole 39 formed between
Lubricating oil is supplied from a radial hole 34 of the force shaft.

Carrier CR and single planetary gear 1
Between the 0 pinion P ₁ , steel washers 40 and 41 are disposed on both sides, and a bronze washer 42 is interposed therebetween. Lubricating oil is positively supplied through radial holes 24 formed in the pinion shaft. Supplied. Further, the lubricating oil supplied to the bearing 44 via the radial hole 43 formed in the input shaft can also be supplied to the washers 32, 38, 42.

Next, the oil discharge structure of the present invention will be described with reference to FIG. The ring gear R ₂ is formed with 18 radial holes 101 through which lubricating oil is supplied to the second brake B _2. One end of the ring gear R ₂ is spline-connected to a clutch hub 102. A locking means 103 is provided and a radial hole 104 for oil discharge.
Are formed.

The clutch hub 102 is disposed radially inward of the ring gear R ₂ and has a single planetary gear 10
, The clutch C ₀ forms a gap 105 adjacent to the second brake B ₂ , and the oil discharged from the radial hole 104 through the gap forms the case 106.
Collected along.

The first ring gear R ₁ is connected to the input shaft 15 via a clutch C ₃ . Ring gear to the other end of the R ₂ ring gear flange 107 is splined 108
By locking means 109 and outer race 112 of the one-way clutch F ₁ is fixed with locked in, in the meantime, the seal ring 110 is disposed. The inner race 111 of the one-way clutch is spline-connected to the case 106. Thrust bearings 113 and 114 are provided on both sides of the ring gear flange 107. The thrust bearing 113 is provided between the ring gear flange 107 and the carrier CR.

Next, the structure of the washer will be described with reference to FIG. Washers 36, 37, 40, and 41 indicate steel washers, and the pinion shaft 20 (FIG. 1) penetrates the circular center hole 45. Washer 3
Reference numerals 8 and 42 denote bronze washers, and a center hole 46 is a circular hole 46 'through which the pinion shaft 20 (FIG. 1) passes.
Further, four oil sump chambers 47a, 47b, 47c, 47d are formed at intervals of 45 ° with respect to the vertical and horizontal axes. Thereby, the washers 36, 37, 38
In the three-phase combination of (3) and the washer (40, 41, 42), the window 47 of the bronze washer at the center is used.
Oil pools are formed at a to 47d, and the washer is sufficiently lubricated.

Next, the operation at each shift speed will be described with reference to FIGS. 5, 6 and 7 while referring to the operation table of the transmission of the present invention. The structure of the washer will be described. At the time of reverse, when the vehicle speed is higher than a predetermined value, C ₂ ,
C ₃ clutch and B ₂ brake is engaged vehicle speed only C _2, C ₃ clutch when less than the predetermined value are engaged.

[0028] In the D range, only C ₁ clutch when first speed is engaged. Moreover, the first and second one-way clutches F ₁ and F ₀ are engaged, and the rotation of the input shaft 15 is controlled by the first clutch C ₁ and the second one-way clutch F _0.
It is transmitted to the small ring gear R ₁ through, and by the first one-way clutch F ₁ in this state, the carrier CR while idly sun gear S since the rotation of the large ring gear R ₂ is blocked is decelerated greatly The decelerated rotation is taken out of the output gear 13. Then, the rotation of the output gear 13 is reduced by the reduction mechanism 51, and further, by the differential device 52, the left and right accelerator shafts 59 a, 59 b
Is transmitted to

[0029] Further, in the second speed state, the first band of the brake B ₁ is tightened. The rotation of the input gear 15
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 ₂ is taken out of the carrier CR as the second rotation while idling. In addition, 1-2
In the shifting prevents the occurrence of shift shock due to clutching by the first one-way clutch F ₁ is overrun. Furthermore, the time of the 2-3 shift engagement with the first timing of the release of the brake B ₁ of the fourth clutch C ₀ are performed properly.

In the third speed state in which 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, the input is Axis 15
Rotation while being transmitted to the small ring gear R ₁ via the second one-way clutch F ₀ and the third clutch C _3, the fourth through the clutch C ₀ is transmitted to the large ring gear R2 planetary gear unit 12 is integral Is taken out from the carrier CR to the output gear 13. At this time, the clutch is re-engaged with the fourth clutch C ₀ and the first brake B _1. However, as described above, an appropriate timing is taken, and a shift through another shift speed is prevented, thereby causing a shift shock. Never.

Next, in the fourth speed state, the first clutch C
_{The first} and fourth clutches C ₀ are in the engaged state, the first brake B ₁ is switched to the locked state, and the third clutch C ₃ is switched to the disengaged state in the fourth speed state. the rotation of the input shaft 15 is transmitted to the large ring gear R ₂ via the fourth clutch C _0, and, since the first sun gear S by the brake B ₁ is is engaged rotation of the large ring gear R ₂ is The carrier CR is rotated at a high speed while the ring gear R ₁ idles, and this rotation is transmitted to the output gear 13.

At this time, the first brake B₁With locking
In both cases, the third clutch C3 is released, but the third clutch C3 is released.
Latch C_ThreeEven if you release it early, the second one-way crack
Chi F ₀As a result, the third gear state is maintained, and therefore the first
Brake B₁By controlling the locking of the
The occurrence of a shift shock due to replacement 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 The second one-way clutch F ₀ is controlled by controlling the release.
The shift from the overrun to the lock is performed, so that the shift can be smoothly performed. Further, if the 3-2 speed downshift, release of the fourth clutch C ₀ is delayed with respect to the first locking of the brake B _1, the fourth clutch C ₀ and the first brake B ₁ is both Shifting through the released first gear state,
That is, a shift operation such as the 3-1-2 speed is prevented.

The operation of the oil discharge structure according to the present invention will be described below. For the fourth speed state as described above is made to achieve the diameter of the pinion P ₁ is a small diameter, the rotational speed is increased, the relative rotational speed between the pinion P ₁ and the carrier CR is caused to increase.

[0035] For example, the rotational speed ratio of the carrier CR to the fourth speed in the present embodiment is 1.361, the rotational speed ratio of the pinion P ₁ single planetary gear with respect to the input rotation about 2.501, the dual planetary small pinion The rotational speed ratios of P ₂ and large pinion P ₁ ′ are 1.863 and 1.2, respectively.
64. Moreover, the number of rotating members in the planetary gear unit 12 is _two sun gears S ₁ and S _2, two ring gears R ₁ and R ₂ , and twelve pinions. Therefore, the radial holes 22, 23, 2
4, needle bearings 48, 49, 48 'and washers 32, 33, 36, 37, 38, 40, 41,
42 is supplied with lubricating oil.

Lubricating oil is also supplied to the thrust bearing 113 between the ring gear flange 107 and the carrier CR. In particular, the thrust bearing 113, washers 32, 33, 36 to 38, needle bearings 48,
The lubricating oil supplied to 8 ′ and 49 stays in the closed space formed by the ring gear R ₂ , the hub 102 and the ring gear flange 107, and the radial hole 1 for lubricating the brake B ₂
01 is a small hole of about 1.5φ,
Eight are formed. Therefore, it always only performs the function of lubricating the brake. Radial bore 104 through the clutch C ₀ and the gap 105 between the brake B ₂ because it is near the spline portions 103, directly flows out into the case 106 is housed in the oil pan along the casing 106 The Rukoto. Further, the ring gear flange 107 supports a seal structure 110 for lubricating the one-way clutch F ₁ and performs relative rotation between the carrier CR and the ring gear R ₂ .
Since by disposing a bearing for supporting respectively dividing the relative rotation between the ring gear R ₂ and the case 106, and thus to further improve the durability of the bearing.

[Brief description of the drawings]

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

FIG. 2 is a sectional view of the carrier lubrication structure of the present invention, taken along the line AA in FIG. 1;
It is sectional drawing.

FIG. 3 is a sectional view of the oil discharge structure of the present invention.

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

FIG. 5 is a full sectional view of the transmission according to the present invention.

FIG. 6 is a skeleton diagram of the transmission according to the present invention.

FIG. 7 is an operation table of the transmission according to the present invention.

[Explanation of symbols]

DESCRIPTION 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 Shaft hole of pinion shaft 22, 23, 24 Radial hole of pinion shaft 26 Locking tool 26 '1st radial direction hole 26 "second radial bore CR carrier _{P 1, P 1 ', P} 2 pinion shaft R ₁ first ring gear S _1, S ₂ sun R ₂ second ring gear F ₁ one-way clutch B ₂ first Brake C ₀ First clutch means 102 First clutch hub 103 Connecting portion 104 Radial hole for oil discharge 105 Clearance 106 Case 107 Ring gear flange 108 Spline connecting portion 113, 114 Thrust bearing

Continuation of the front page (72) Inventor Fumitomo Yokoyama 10 Takane, Fujii-machi, Anjo-shi, Aichi Examiner Aisin AW Co., Ltd. Examiner Shogo Tanai (56) References JP-A-61-45171 (JP, A) JP-A-61-41052 (JP, A) JP-A-2-89871 (JP, A) JP-A-2-89870 (JP, A) (58) Fields investigated (Int. Cl. ⁶ , DB name) F16H 57/00-57/04 F16H 3/44-3/78 F16H 25/12

Claims (5)

(57) [Claims] An input shaft for transmitting an engine driving force; a planetary gear unit connected to the input shaft; a plurality of friction engagement elements connected between elements of the planetary gear unit to achieve a plurality of shifts; A vehicle transmission comprising an output shaft connected to one element of a planetary gear unit, comprising: a first clutch means connected between a first ring gear of the planetary gear unit and the input shaft; The vehicle transmission according to claim 1, wherein a hub of the clutch is disposed radially inward of the ring gear, and a radial hole for discharging oil is disposed at a connection control portion between the hub and the ring gear. 2. The planetary gear unit is provided adjacent to the single planetary gear, the single planetary gear is connected to a sun gear, and the carriers are connected to each other.
A dual planetary gear having a first ring gear connected to the carrier via a double pinion, wherein the carrier is connected to the output shaft, and a second ring gear of the single planetary gear is connected via a second clutch means; 2. The transmission according to claim 1, wherein the hub is disposed radially outward of the second ring gear, the hub being connected to the input shaft. 3. A first radially outer side of the first ring gear.
And a predetermined gap is formed between the first clutch and the first brake, a radial hole of the first ring gear is formed in the gap, and oil is passed through the hole. 3. The vehicular transmission according to claim 2, wherein the fluid flows toward the case. 4. A one-way clutch is disposed at an end of the first ring gear opposite to the hub, and a ring gear flange is disposed between the one-way clutch and the planetary gear unit to connect a spline to the first ring gear. 4. The vehicle transmission according to claim 3, wherein the transmission is provided. 5. A first bearing is disposed between the flange and the dual planetary gear, and a second bearing is disposed between the flange and a case to which an inner race of the one-way clutch is connected. 5. The vehicle transmission according to claim 4, wherein: