JP2679019B2 - Gear mechanism of automatic transmission - Google Patents

Description

TECHNICAL FIELD The present invention relates to an automatic transmission, and more particularly to an automatic transmission mounted on an automobile, and more specifically, an input member, an output member, a plurality of planetary gears, and each of these elements. The present invention relates to a combination / arrangement of a clutch and a brake that connects or locks.

(B) Conventional technology Recently, automatic transmissions have been multi-staged due to demands such as further improvement of fuel efficiency and drivability.
Forward 4th, 5th or higher gears have been devised.

As an automatic transmission for four forward speeds, for example, Japanese Patent Laid-Open No. 59-183
As shown in Japanese Patent No. 147, there is a split type based on a Simpson gear train. The automatic transmission 1
As shown in FIG. 8, is composed of a first single planetary gear G ₁ and a second single planetary gear G ₂ , a carrier CR ₁ of the first planetary gear, a ring gear R ₂ of the second planetary gear and an output member O. A first clutch C ₁ between the input member I and the ring gear R _{1 of} the first planetary gear G ₁ and a second clutch between the input member I and the sun gear S ₁ of the _first planetary gear. the C ₂ interposed respectively, further the third clutch C ₃ disposed between the sun gear S _1, S ₂ of the first and second planetary gear, and the sun gear S ₁ of the first planetary gear of the second planetary gear first to fourth interposed clutch C _4, also engaging the carrier CR ₂ of the second planetary gear between the carrier CR ₂
And a second brake B ₂ to lock the brake B ₁ and the sun gear S _2.

Then, the split type automatic transmission 1 is
It operates according to the operation table shown in the figure. That is, in the 1st to 3rd speeds and in reverse, the third clutch C ₃ is connected and the sun gears S ₁ and S _{2 of} both planetary gears are connected to each other to operate similarly to a normal Simpson type (in the 3rd speed, 2 planetary gears
(G ₂ is not involved, so 3rd clutch C ₁ can be released),
At the 4th speed, the first clutch C ₁ and the third clutch C ₃ are released, and the rotation of the input member I is transmitted to the second planetary gear G ₂ via the second clutch C ₂ and the fourth clutch C _4. In conjunction with the stop of the sun gear S ₃ based on the second brake B ₂ , the overdrive rotation from the ring gear R ₂ is taken out by the output member O.

On the other hand, as an automatic transmission with five forward speeds, US Pat.
There is one disclosed in Japanese Patent No. 6,031. The automatic transmission 2
Has three single planetary gears G ₁ , G ₂ , and G ₃ as shown in FIG. 10, and connects the carrier CR ₁ of the first planetary gear and the ring gear R ₂ of the second planetary gear, Further, the carrier CR ₂ of the _second planetary gear and the ring gear R ₃ of the third planetary gear are connected. Then, the rotation of the input member I is transmitted through the first clutch C ₁ to the sun gears S ₁ , S ₂ , S _{3 of} the first, second and third planetary gears.
Is transmitted to the first clutch via the second clutch C ₂ .
Is transmitted to the carrier CR ₁ of the planetary gear and the ring gear R ₂ of the second planetary gear, and is also transmitted to the ring gear R ₁ of the first planetary gear via the third clutch C ₃ , and further to the carrier of the third planetary gear. CR ₃ is connected to the output member O. In addition, each ring gear R ₁ , R ₂ ,
R ₃ is stoppable by the brake B _1, B _2, B ₃ respectively.

Then, the 5-speed automatic transmission 2 operates according to the operation table shown in FIG. That is, in the 1st speed, the third brake B ₃ operates and the third planetary gear G ₃ functions,
At the time of high speed, the second brake operates and the second and third planetary gears G ₂ and G ₃ function, and at the time of third speed, the first brake B ₁ operates and the first, second, and The third planetary gears G ₁ , G ₂ , G ₃ function. Then, in the 4th speed state, the first clutch C ₁ and the second clutch C ₂ are both connected to output a direct-coupled rotation, and in the 5th speed, the first clutch C is output in the 1st to 4th speeds. _What was input to the sun gear from ₁
The carrier CR ₁ and the ring gear R ₂ are input from the second clutch C ₂ and a predetermined overdrive is output. In addition, input from the third clutch C ₃ or the second clutch C ₂ to brake.
B _3, B ₂ and combined is in the third speed reverse is obtained.

(C) Problems to be Solved by the Invention By the way, the split type automatic transmission 1 based on the above-mentioned Simpson type has 12 speed, 23 speed, 34 speed,
When upshifting or downshifting by one speed and one shift, the clutches C ₁ and C ₂ from the input member I do not change grips, but upshifting by skipping from 1 to 4 speed and 2 to 4 speed , Or 4 → 2 speed, and 4 → 1 speed, when kicking down, the first clutch C ₁ and the second clutch from the input member I
C ₂ need arises to replace gripping, with the further third speed fourth speed shift up and shift down, the first clutch C ₁ and it becomes necessary to replace grasp the fourth clutch C _4, of the engine due to timing failure blown up And a shock may occur, and extremely complicated control is required to match the switching timings of both clutches.

It should be noted that the above-described grip change of the input clutch to which the torque from the input member is transmitted has an influence on the shift shock more than the grip change by the brake because the torque capacity of the input clutch is set to be larger than that of the brake. Is big.

Similarly, the above-mentioned automatic transmission 2 of the fifth speed is also used for forward input 2
The individual clutches C ₁ and C ₂ do not cause the clutch change when shifting up or down one gear each of 12th gear, 23rd gear, 34th gear and 45th gear, but 15th gear, 25th gear
In the case of jumping up or kicking down by jumping to the 35th speed and the 35th speed, it becomes necessary to grab the first clutch C ₁ and the second clutch C ₂ that receive the torque from the input member I.

In particular, due to the large displacement engines installed in passenger cars, high performance engines such as twin cams and turbos, and the expansion of the range of application of automatic transmissions such as those installed in trucks, large torque has been automatically increased. In the case of acting on the transmission, the problem caused by the change of the input clutches C ₁ and C ₂ is conspicuous.

Therefore, in the present invention, in addition to the deceleration stage and the direct coupling stage and the speed increasing stage at the time of forward movement, a wide gear is achieved and the clutch (input clutch) that receives torque from the input member is not gripped, thereby eliminating the above problem. The purpose is to eliminate points.

(D) Means for Solving the Problems The present invention has been made in view of the above circumstances. For example, referring to FIGS. 1 to 7, the input member (I) and the output member ( O) and at least the first and second
Automatic transmission including a single planetary gear (G ₁ ) (G ₂ ) and a clutch and a brake that appropriately connect or lock the input member, the output member, and the predetermined elements of the first and second single planetary gears. Gear mechanism (11,12,1
A 3), the ring gear of the first planetary gear (G ₁₎ (R ₁₎
And said second planetary gear (G ₂₎ of the carrier (CR ₂₎
And the output member (10) are connected to each other, and the torque of the input member (I) is controlled by the ring gear (R ₂ ) of the _second single planetary gear and the carrier (CR ₁ ) of the first single planetary gear. A second clutch (C ₂ ) interposed between at least the input member (I) and the carrier (CR ₁ ) of the first planetary gear, and the first planetary gear. Sun gear (S ₁ ) and second planetary gear sun gear (S ₂ )
A first brake (B ₁ ), which has a third clutch (C ₃ ) interposed between the first and second clutches (C ₃ ) and locks at least the carrier (CR ₁ ) of the first planetary gear,
And a second brake (B ₂ ) for locking the sun gear (S ₁ ) of the _first planetary gear, and in the deceleration position, the both sun gears are passed through the _third clutch (C ₃ ). The rotation of the input member (I) is transmitted via the ring gear (R ₂ ) of the second single planetary gear in a state where (S ₁ , S ₂ ) are connected, and the first or second brake is also transmitted. (B ₁ , B ₂ ) are appropriately operated to transmit power to the output member (O), and when the input member (I) and the output member (O) are directly connected, the third clutch (C ₃ ) Through the two sun gears (S ₁ , S ₂ ) are connected, the input member (I)
Rotation of the second planetary gear ring gear (R ₂ )
And to the carrier (CR ₁ ) of the first planetary gear via the second clutch (C ₂ ),
Both planetary gears (G ₁ , G ₂ ) are directly connected to the input member and the output member, and in the speed increasing position, the third clutch (C ₃ ) is released to release both sun gears (S ₁ , S 2). _{With 2} ) separated,
And transmitting rotation of said input member (I) to the carrier (CR ₁₎ of the through the second clutch (C ₂₎ a first single planetary gear, idly sun gear (S ₂₎ of said second planetary gear At the same time, the second brake (B ₂ ) is operated to increase the speed exclusively by the first single planetary gear (G ₁ ) and the power is transmitted to the output member (O). It is in the mechanism.

Further, as an example of the gear mechanism 12 in which a one-way clutch is interposed in order to prevent a shift shock due to a brake and clutch switching operation, as shown in FIG. 3, the second planetary gear (G ₂ the first clutch (C ₁₎ interposed between the ring gear (R ₂₎ of), and the first one-way clutch F ₁ and interposed between the first carrier CR ₁ and the fixed portion of the planetary gear G ₁ and said first sun gear S ₁ of the planetary gear G ₁ and the second planetary gear
A second one-way clutch F ₂ is interposed between the sun gear S _{2 of} G _{2 and} the sun gear S of the _second planetary gear G ₂ .
_{2 is provided} with a third brake B ₃ which locks one-way rotation through a third one-way clutch F ₃ .

The first clutch C ₁ interposed between the input member I and the ring gear R _{2 of} the second planetary gear G ₂ continues to maintain the connected state during forward movement, and thus the forward movement shown in FIGS. 1 and 3 is performed. It does not have any meaning in the case of a four-speed transmission, but it is necessary when the fifth forward speed is reversed as described below.

Next, showing an example of the gear mechanism 13 of the forward 5th speed automatic transmission, as shown in FIG.
The third single planetary gear G ₃ a is attached to the lowest speed (i.e., first speed) and a reverse, the planetary gear G ₃ are, the carrier CR ₃ second planetary gear G ₂ of the carrier CR ₂ and the output member O (hence the 1 planetary gear G _{1 also to} the ring gear R ₁ ), and the sun gear S ₃ together with the ring gear R ₂ of the second planetary gear G ₂ to the first clutch C ₁ which connects to the input member I, and the ring gear R ₃ is connected to 4th brake B ₄ .

Furthermore, when a one-way clutch is interposed in order to prevent a shift shock due to a brake and clutch switching operation, the first clutch C ₁ , the second clutch C ₂ , the third clutch C ₃ , the first brake B ₁ , and the second clutch C ₁ , In addition to the brake B ₂ and the fourth brake B ₄ , a fifth clutch C _{5 provided} between the output side of the second clutch C ₂ and the sun gear S _{1 of} the first planetary gear G ₁ is provided. carrier CR ₁ and該該1 planetary gear G ₁ of the fifth brake B ₅ and the first locking the rotation in one direction through the carrier CR ₁ a first one-way clutch F ₁ of the first planetary gear G ₁ The fourth clutch C ₄ is disposed between the _first one-way clutch F ₁ and the one-way clutch F ₁ and the sun gear S ₂ of the _second planetary gear G ₂ is locked via the third one-way clutch F ₃ in one direction. 3 brake B ₃ are disposed, and wherein 1 of the sun gear of the planetary gear G ₁
S ₁ and the second between the sun gear S ₂ of the second planetary gear G ₂
Interposed a one-way clutch F _2, also formed by interposing a fourth one-way clutch F ₄ between the fixed member and the ring gear R ₃ of the third planetary gear G _3.

(E) based on the action described configuration, state In the reduction stage (e.g. 1-speed and 2-speed), which both sun gears to connect the third clutch (C ₃₎ to (S _1, S ₂₎ connected together Then, the rotation of the input member (I) is changed to the ring gear (R ₃ ) of the second planetary gear (G ₂ ).
And outputs a predetermined decelerated rotation to the output member (O) by operating the first or second brake (B ₁ , B ₂ ).

In the direct connection stage (for example, 3rd speed), the rotation of the input member (I) is changed to the second rotation while the third clutch (C ₃ ) is connected and both sun gears (S ₁ , S ₂ ) are integrally connected. Input to the ring gear (R ₂ ) of the planetary gear of the first planetary gear and the carrier (C) of the first planetary gear via the second clutch (C ₂ ).
It is transmitted to R ₁ ), and both planetary gears (G ₁ , G ₂ ) are integrated to output the direct-coupled rotation to the output member (O).

Then, in the speed-increasing stage, the rotation of the input member (I) is changed to the rotation of the first planetary gear in a state where both sun gears (S ₁ , S ₂ ) are separated by releasing the third clutch (C ₃ ). By transmitting to the carrier (CR ₁ ) and locking the sun gear (S ₁ ) by the operation of the second brake (B ₂ ), the ring gear (R ₁ ) of the planetary gear (G ₁ ) is rotated at an increased speed to increase the speed. The rotation outputs to the output member (O). At this time, the sun gear (S ₂ ) of the second planetary gear (G ₂ ) is in the free state, and the second planetary gear (G ₂ ) does not participate in the speed change at all and is not connected to the input member (I). With the ring gear (R ₂ ) still in the connected state, the sun gear (S ₂ ) idles and the speed-increasing rotation of the ring gear (R ₁ ) of the first planetary gear is directly output through the carrier (CR ₂ ) to the output member. Transfer to (O).

As a result, continuous upshifting and downshifting, as well as stepped states (14th speed, 24th speed, 15th speed)
Even in upshifts and kickdowns in the 25th and 25th speeds, the shift shock due to the torque change from the input member does not occur.

Specifically, the forward fourth speed gear mechanism 11 shown in FIG.
Operates as shown in the operation table shown in FIG. _2, and the rotation is always transmitted from the input member I to the ring gear R ₂ of the second planetary gear G _2.
The rotation of R ₂ idles the sun gear S ₂ via the carrier CR ₂ .

The gear mechanism 12 shown in FIG. 3 operates according to the operation table shown in FIG. 4, and operates in the first clutch C _{1 at} the first speed, the third brake B ₃ at the second speed, and the second clutch C at the third speed. _{When in 2nd} and 4th speed, the second brake B ₂ is operated in sequence, and 1st speed → 2nd speed → 3rd speed →
Fourth speed is achieved.

Similarly, the forward fifth speed gear mechanism 13 shown in FIG. 5 operates according to the operation table shown in FIG. That is, in the 1st speed, the third planetary gear G ₃ functions exclusively, and the rotation from the input member I is taken out as the decelerated rotation to the carrier CR ₃ via the sun gear S ₃ and output to the output member O. Therefore, only by replacing only the first planetary gear G ₃ , it is possible to freely set only the gear ratio of the first speed, which has a great influence on the engine torque and the like. Then, the first clutch C _{1 at} the first speed, the fourth clutch C ₄ at the second speed, the third brake B ₃ at the third speed, the second clutch C ₂ at the fourth speed, and the second brake B ₂ at the fifth speed are sequentially operated. Thus, 1 → 2 speed, 2 → 3 speed, 3 → 4 speed, and 4 → 5 speed are achieved.

(F) Embodiment Gear mechanism 11 for a forward four-speed automatic transmission, which is the basis of the present invention 11
As shown in FIG. 1, includes an input member I, an output member O, and first and second single planetary gears G ₁ and G ₂ . Then, the ring gear R of the first planetary gear G _1
1 (abbreviated as _1st ring gear R ₁ below) and 2nd
Carrier CR ₂ and the output member O are integrally connected, and the input member I is connected to the second ring gear R ₂ and the first carrier is connected via the second clutch C _2.
Connected to CR ₁ . Further, the third clutch C ₃ is interposed between the first sun gear S ₁ and the second sun gear S _2, and the first carrier CR ₁ can be appropriately locked by the first brake B ₁ . Moreover, the first sun gear S ₁ can also be appropriately locked by the second brake B ₂ .

The basic gear mechanism 11 for the fourth forward speed operates as shown in the operation table of FIG.

That is, at the 1st speed, the third clutch C ₃ and the first brake B ₁
Are engaged and the others are released. In this state,
The rotation of the input member is transmitted to the second ring gear R ₂ and
To the carrier CR ₂ of the second pinion P ₂ ,
Rotational force is applied to the first carrier CR ₁ via the second sun gear S ₂ and the first sun gear S ₁ . However, since the first carrier CR ₁ is stopped by the first brake B ₁ , the first ring gear R ₂ is rotated together with the second carrier CR ₁ via the first pinion P ₁ and output. The decelerated rotation is taken out to the member O.

In addition, in the second speed, the second brake B ₂ operates in addition to the connection of the third clutch C ₃ . In the this state, the input rotation transmitted second ring gear R ₂ from member I is decelerated rotation is taken out to the carrier CR ₂ with the stop the second sun gear S _2, the output member O Output.

Further, in the third speed, that is, in the direct connection state, the third clutch C ₃
At the same time, the second clutch C ₂ is connected. In this state, the rotation from the input member I is transmitted to the first carrier CR ₁ and also to the second ring gear R ₂ , so that the sun gears S ₁ and S _{2 of the} planetary gears G ₁ and G ₂ are connected to each other. Also, because of the fact that the first ring gear R ₁ and the second carrier CR ₂ are integrally continuous, both planetary gears G ₁ and G ₂ rotate integrally, and the direct coupling rotation causes the output member O to rotate. Is output to.

Then, in the fourth speed state, that is, in the overdrive state, the second brake B ₂ operates in addition to the connection of the second clutch C ₂ . In this state, the rotation of the input member I is the first
Is transmitted to the carrier CR ₁ of the ring gear R ₁ and the increased rotation is taken out from the ring gear R ₁ based on the stop of the first sun gear S ₁ , and the rotation is output to the output member O via the second carrier CR ₂ .
At this time, in the second planetary gear G ₂ , the ring gear
Sun gear S ₂ overruns with the input rotation of R ₂ , but
The sun gear S ₂ and the ring gear R ₂ only idle and do not participate in power transmission.

Therefore, at the time of forward movement, the rotation may be transmitted from the input member O to one planetary gear G ₂ at all times, and the torque from the input member I may be connected / disconnected only by the second clutch C ₂ , and the input clutch may be replaced. Does not occur.

It should be noted that the fourth speed gear mechanism 11 cannot realize the reverse drive state only by the mechanism, but can easily realize the reverse drive state by attaching a back gear or the like.

Next, with reference to FIG. 3, a description will be given of the fourth speed gear mechanism 12 which prevents a shock due to switching of clutch and brake operation.

This gear mechanism 12 is the same as the gear mechanism 11 except that the first carrier
First one-way clutch F ₁ interposed between CR ₁ and the fixing member, the second one-way clutch F ₂ is interposed between the sun gear S ₂ of the first sun gear S ₁ and the second and, second sun gear S _{A second} brake B ₃ for locking ₂ through the third one-way clutch F ₃ is additionally provided. The input member I
First clutch C ₁ interposed between the second ring gear R ₁ and the second ring gear R ₁
Are all connected when moving forward, but are required when moving backward (explained in the next 5th gear mechanism).

Then, the fourth forward speed gear mechanism 12 operates as shown in FIG. The solid circles indicate the operation in the D range, and the broken circles indicate the operation in the engine brake operating state.

In the first speed state, the first clutch C ₁ is in the connected state. In this state, the rotation of the input member I is transmitted second to the ring gear R _1, the sun gear S ₂ via the pinions P ₂
The rotational biasing force acting on the first carrier CR ₁ is transmitted to the first sun gear S ₁ via the second one-way clutch F _2, and the rotational biasing force of the first carrier CR ₁ via the pinion P ₁ is applied to the first one-way clutch F 1. Regulated by ₁ and therefore the second ring gear R ₂
The rotation is distributed to the second planetary gear G ₂ and the first planetary gear G ₂ , and is taken out to the output member O via the first ring gear R ₁ and the second carrier CR ₂ which are integrally configured.

Further, in the second speed state, the third brake B ₃ in addition to the first clutch C ₁ is operated. In this state, the rotation of the input member I is transmitted to the second ring gear R _2, and the decelerated rotation is further reduced by the second sun gear S _{2 in} the locked state via the third one-way clutch F _3. Taken out to ₂ ,
Output to the output member O.

Further, in the third speed state, that is, in the direct connection state, the second clutch C ₂ is connected in addition to the first clutch C ₁ and the third brake B ₃ . In this state, the second ring gear R ₂ and the first ring gear R ₂
The rotation from the input member I is transmitted to the carrier CR ₁ of the second carrier CR 1 and the _second carrier CR ₂ and the first ring gear R ₁ are integrally connected, and both sun gears are connected via the _second one-way clutch F _2. Based on the connection of S ₁ and S ₂ , the first planetary gear G ₁ and the second planetary gear G ₂ rotate together, and the direct connection rotation is output to the output member O. The third brake B ₃ is in a locked state, there is no possibility that the third one-way clutch F ₃ are integrally rotated in the second sun gear S ₂ is prevented.

In the fourth speed state, the first clutch C ₁ and the third clutch
In addition to brake B ₃ and second clutch C ₂ , second brake B ₂
Operates. In this state, the rotation of the input member I is transmitted to the first carrier CR ₁ , and the first sun gear S ₁ is in the fixed state, so that the increased rotation of the ring gear R ₁ is extracted. The high speed rotation is output to the output member O via the second carrier CR ₂ . At this time, even if the input rotation is applied to the second ring gear R ₂ through the first clutch C ₁ , the sun gear S ₂ idles due to the second one-way clutch F _2, so that the second planetary gear G ₂ is There is no regulation of power transmission.

To operate the engine brake, the third clutch C ₃ and the first brake B ₁ are operated in the first speed,
Also In the second speed and third speed state and third clutch C _3, it acts similarly to the gear mechanism 11 previously shown.

Therefore, the fourth speed gear mechanism 12 does not change the grip of the input clutches C ₁ and C ₂ when moving forward, and in the D range, it does not shift when shifting up or down by one step. It suffices to operate or release the clutches or brakes one by one, and since the one-way clutch is interposed when stopping all the elements of the planetary gears, the shift shock due to the grip change is reliably prevented.

Next, the gear mechanism 13 for the fifth forward speed and the first reverse speed will be described.

The basic gear train of this gear mechanism 13 is the gear mechanism shown in FIG.
11, a third single planetary gear G ₃ is additionally provided, and the planetary gear G ₃ has a carrier CR ₃ whose second carrier CR ₂ and first ring gear R ₁ which is integral with the second carrier CR _2.
Then, it is connected to the output member O, the sun gear S ₃ is connected to the first clutch C ₁ together with the _second ring gear R ₂ , and the ring gear R ₃ is further connected to the fourth brake B ₄ .

Further, in order to prevent a shift shock due to the brake and clutch switching operation, and with the realization of the reverse drive, the gear mechanism 13 is fixed to the first one-way clutch F ₁ in addition to the gear mechanism 12 shown in FIG. A fifth brake B ₅ is arranged between the member and the first one-way clutch F ₁ and the first one.
The fourth clutch C ₄ is interposed between the carrier CR ₁ and the carrier CR ₁ and the fifth clutch C ₅ is interposed between the output side of the second clutch C ₂ and the first sun gear S ₁ , and The fourth one-way clutch F ₄ is interposed between the ring gear R ₃ and the fixed member.

Then, the fifth speed gear mechanism 13 operates according to the operation table shown in FIG.

That is, in the first speed state, the first clutch C ₁ and the fifth clutch C ₁
Brake B ₅ is activated. In the this state, rotation of the input member I is transmitted to the third sun gear S _3, based on the in the fourth one-way clutch F ₄ rotation of third ring gear R ₃ is blocked, the third The decelerated rotation is taken out from the carrier CR _{3 of} and output to the output member O. At this time, the input rotation is also applied to the second ring gear R ₂ , but the sun gear S ₂ idles and does not participate in the transmission at all.

The second speed state corresponds to the first speed of the above-described embodiment, but the fourth clutch C ₄ is engaged in addition to the operation of the first clutch C ₁ and the fifth brake B ₅ . In this state, the rotation of the input member I is transmitted to the second ring gear R ₂ , and the second one-way clutch F ₂ integrally rotates the second sun gear S ₂ and the first sun gear S _1. Further, the first carrier CR ₁ is prevented from rotating by the first one-way clutch F ₁ via the fourth clutch C ₄ , and the first and second planetary gears G ₁ and G ₂ function in the same manner as described above to output the output member. Decelerated rotation is transmitted to O. At this time, the third carrier CR ₃ also rotates integrally with the output member O, but the ring gear R ₃ idles by the fourth one-way clutch F ₄ and does not participate in power transmission at all.

Further, the third speed state, which correspond to the second speed of the previous embodiment, the first clutch C _1, the fifth brake B _5, in addition to the operation of the fourth clutch, the third brake B ₃ operation To do. In this state, the second ring gear R ₂ from the input member I
Based on the sun gear S ₂ whose rotation is blocked by the third one-way clutch F ₃ , the rotation is extracted from the carrier CR ₂ as decelerated rotation, and the rotation is output.

The fourth speed state is a direct connection state, and the first clutch
C ₁ , 5th brake B ₅ , 4th clutch C ₄ , 3rd brake B ₃
In addition, the second clutch C ₂ is engaged. In this state, the rotation from the input member I is applied to the second ring gear R ₂ and also to the first carrier CR ₁ ,
Since the ring gear R ₁ and the second carrier CR ₂ are integrally configured, the first planetary gear G ₁ and the second planetary gear G ₂ cooperate with each other to integrally rotate, and the direct coupling rotation is the output member. It is taken out to O.

Furthermore, the 5th speed state corresponds to the 4th speed of the previous embodiment, and
In addition to the operation of the clutch C ₁ , the fifth brake B ₅ , the fourth clutch C ₄ , the third brake B ₃ , and the second clutch C ₂ , the second brake B ₂ operates. In this state, since the rotation of the input member I is transmitted to the first carrier CR ₁ and the sun gear S ₁ is stopped, the speed-increasing rotation is taken out from the ring gear R ₂ and the speed-increasing rotation is taken out. Is the second and third carriers CR ₂ , CR
It is output to the output member O via ₃ .

Then, in the reverse drive state, the second clutch C ₂ , the fifth clutch C ₅ , and the fourth brake B ₄ are operated. In this state, the input member rotates the second clutch C ₂ of I, is transmitted second to the sun gear S ₂ via the fifth clutch C ₅ and the second one-way clutch F _2, further third ring gear R ₃ of stops Based on this, the second and third carriers CR ₂ and CR ₃ integrally formed are reversed and taken out from the output member O.

The above operation is shown in the velocity diagram in FIG.

On the other hand, in order to act during engine braking, the fourth brake B ₄ is operated at the first speed to completely stop the third ring gear R ₃ , and at the second speed, the third clutch C ₃ is connected. The first and second sun gears S ₁ and S ₂ are completely connected, and the first brake B ₁ is operated to completely stop the _first carrier CR ₁ . Similarly, in the third speed, the third clutch C ₃ is connected and the second brake B ₂ is actuated in the same manner as the first clutch C ₃ .
Stop Sun Gear S ₁ completely. Then, in the 4th speed, the third clutch C ₃ is connected to completely connect both planetary gears G ₁ and G ₂ . Moreover, during reverse travel connects the third clutch C _3, completely connecting the input member I and the second sun gear S _2.

Therefore, in the forward fifth speed gear mechanism 13, the input clutches C ₁ and C ₂ are not grabbed when the vehicle is moving forward.
In the range, it is sufficient to operate or release the clutch or brake one by one when upshifting or downshifting one step at a time, and since the one-way clutch is interposed when stopping all the planetary gear elements, Shock due to re-grabbing is completely prevented. Further, the first speed is dependent on only the third planetary gear G _3, may set the gear ratio arbitrarily by changing with the planetary gear G _3.

(G) Effects of the Invention As described above, according to the present invention, the rotation of the input member is controlled by the carrier (CR ₁ ) of the _first planetary gear and the second planetary gear.
It is configured so that it can be transmitted to the ring gear (R ₂ ) of the planetary gears, and when in the direct connection position, power is transmitted to the elements of both planetary gears, and both gears cooperate to transmit integral rotation. At the speed increasing position, the speed is exclusively transmitted by the first planetary gear and transmitted to the output member. Therefore, even in the high speed position, the rotation of the predetermined element of the second planetary gear is maintained. Yes, when moving forward, the clutch does not change the rotation from the input member,
It is possible to prevent the occurrence of shift shock due to the change of the input clutch when the gear is jumped up and kicked down.

As a result, a deceleration stage, a direct connection stage and an acceleration stage are achieved.
It is possible to make the automatic transmission wide gear, but it is not necessary to re-grip the input clutch that receives the torque from the input member when moving forward, and to eliminate the shock caused by the re-grip of the input clutch. You can

Further, when the first, second and third one-way clutches F ₁ , F ₂ , F _{3 and} the third brake B ₃ are provided as in claim ₂ , one clutch is provided from the first speed to the fourth speed. Alternatively, the brakes may be sequentially actuated, and the one-way clutch intervenes when stopping each element of the planetary gear, so that the operation becomes extremely easy and the occurrence of shift shock due to all grip changes can be prevented.

Further, as described in claim 3, when the third single planetary gear G ₃ is added, the multi-speed shift with the lowest speed added becomes possible.

And, as described in claim 4, the first, second and third
Elements of the planetary gears G ₁ , G ₂ , G ₃ and clutches C ₁ , C
_{When 2} , C ₃ and brakes B ₁ , B ₂ , B ₄ are installed, the input clutch
A forward 5th speed / reverse 1st speed gear mechanism that does not change the grip of C ₁ and C ₂ can be configured, and since the third planetary gear G ₃ operates independently in forward 1st speed, the engine power characteristics and exhaust The gear ratio for 1st speed, which is greatly affected by the difference in capacity and vehicle type such as trucks and passenger cars, can be set arbitrarily by simply replacing the third planetary gear G ₃ , and other gear mechanisms can be set.
The third planetary gear G with G ₁ and G ₂ held
By converting ₃ , the applicable range of this 5-speed automatic transmission can be greatly and easily expanded.

Furthermore, as claimed in claim 5 wherein the first, second, third and fourth one-way clutch F _1, F _2, F _3, F _4, the fourth and fifth clutch C _4, C ₅ and the fifth brake If B ₅ is installed, one clutch or brake can be operated sequentially from the 1st speed to the 5th speed, and a one-way clutch is used to stop each element of the planetary gear, which makes the operation extremely easy. , It is possible to prevent the occurrence of shift shock due to all grip changes.

[Brief description of the drawings]

FIG. 1 is a schematic view showing the basics of a fourth forward speed gear mechanism according to the present invention, and FIG. 2 is a view showing its operation. Also, the third
FIG. 4 is a schematic view showing an embodiment of a forward fourth speed gear mechanism, and FIG. 4 is a view showing its operation. Furthermore, Fig. 5 shows 5 forward speeds.
FIG. 6 is a schematic diagram showing an embodiment of a reverse first speed gear mechanism, FIG. 6 is a diagram showing its operation, and FIG. 7 is its velocity diagram. FIG. 8 is a schematic diagram showing a conventional fourth forward speed gear mechanism, and FIG. 9 is a diagram showing its operation. And
FIG. 10 is a schematic view showing a conventional 5th forward speed gear mechanism, and FIG.
The figure shows the operation. 11 …… Forward 4 speed gear mechanism (basic), 12 …… Forward 4 speed gear mechanism, 13 …… Forward 5 speed / reverse 1 speed gear mechanism, I …… Input member, O …… Output member, G ₁ …… 1st single planetary gear, G ₂ ... 2nd single planetary gear, G ₃ ...
Third single planetary gear, R ₁ , R ₂ , R ₃ ...... Ring gear, S ₁ , S ₂ , S ₃ ...... Sun gear, CR ₁ , CR ₂ , CR ₃ …… Carrier, P ₁ , P ₂ , P ₃ ...... Pinion, C ₁ …… First clutch, C ₂ …
... 2nd clutch, C ₃ ... 3rd clutch, C ₄ ... 4th clutch, C ₅ ... 5th clutch, B ₁ ... 1st brake, B ₂ ...
... 2nd brake, B ₃ ... 3rd brake, B ₄ ... 4th brake, B ₅ ... 5th brake, F ₁ ... 1st one-way clutch, F ₂ ... 2nd one-way clutch, F ₃ ... … Third one-way clutch, F ₃ … Third one-way clutch.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-60-65942 (JP, A) JP-A-49-104063 (JP, A) JP-A-49-111072 (JP, A) Actual development Sho-57- 107044 (JP, U) JP47-2326 (JP, B1) JP48-251 (JP, B1) JP47-28825 (JP, B1)

Claims (5)

(57) [Claims] 1. An input member, an output member, and at least a first member.
And a second single planetary gear, and a clutch and a brake that appropriately connect or lock the input member, the output member, and the predetermined elements of the first and second single planetary gears, and a gear mechanism of the automatic transmission. The ring gear of the first planetary gear, the carrier of the second planetary gear, and the output member are mutually connected, and the torque of the input member is changed to the ring gear of the second single planetary gear and the first single. A second clutch which is configured to be transmitted to the carrier of the planetary gear, and wherein the clutch is interposed at least between the input member and the carrier of the first planetary gear,
And a third clutch interposed between the sun gear of the first planetary gear and the sun gear of the second planetary gear, wherein the brake locks at least the carrier of the first planetary gear, and the first clutch. A second brake for locking the sun gear of the first planetary gear; and, in the deceleration position, the rotation of the input member is changed to the second speed with the both sun gears connected via the third clutch. Of the single planetary gear is transmitted through the ring gear, and the first or second brake is appropriately operated to transmit power to the output member. Further, when the input member and the output member are directly connected, The rotation of the input member is transmitted to the ring gear of the second planetary gear in a state where both sun gears are connected via a three-clutch. Both of them are transmitted to the carrier of the first planetary gear through the second clutch so that both planetary gears are directly connected to the input member and the output member. Further, in the speed increasing position, the third clutch is released. And the two sun gears are separated from each other, the rotation of the input member is transmitted to the carrier of the first single planetary gear via the second clutch, and the sun gear of the second planetary gear is idled while (2) A gear mechanism of an automatic transmission, wherein two brakes are operated and the speed is exclusively increased by the first single planetary gear to transmit power to the output member. 2. A first clutch is interposed between the input member and a ring gear of the second planetary gear, and a first clutch is provided between the carrier and the fixed portion of the first planetary gear.
A one-way clutch is interposed, and a second one-way clutch is interposed between the sun gear of the first planetary gear and the sun gear of the second planetary gear, and the second one-way clutch is interposed.
The gear mechanism of the automatic transmission according to claim 1, wherein the sun gear of the planetary gear is provided with a third brake that locks one-way rotation through a third one-way clutch. 3. An input member, an output member, a first, second and third single planetary gears, and a predetermined element of the input member, the output member, the first, second and third single planetary gears, which are appropriately connected. A gear mechanism of an automatic transmission, comprising: a clutch and a brake that are locked, the ring gear of the first planetary gear, the carrier of the second planetary gear, the carrier of the third planetary gear, and the output. The second member connected to each other,
The planetary gear ring gear and the third planetary gear sun gear are integrally connected, and the torque of the input member is connected to the second planetary gear ring gear and the third planetary gear sun gear via the first clutch. , The second planetary gear carrier is connected to the first planetary gear carrier via a second clutch, and the first planetary gear sun gear and the second planetary gear sun gear are connected to each other via a third clutch. The rotation of the input member to the first
The power is transmitted to the sun gear of the third single planetary gear via a clutch, the ring gear of the third single planetary gear is locked by the brake, and is decelerated exclusively by the third planetary gear to power the output member. In the transmission position and the deceleration position, the rotation of the input member is transmitted to the ring gear of the second single planetary gear via the first clutch in a state where the both sun gears are connected via the third clutch. First to be transmitted via
The planetary gear carrier or sun gear is locked by the brake to transmit power to the output member, and when the input member and the output member are directly connected, the both sun gears are connected via the third clutch. In this state, the rotation of the input member is transmitted to the ring gear of the second planetary gear and the sun gear of the third planetary gear via the first clutch, and to the carrier of the first planetary gear via the second clutch. Communicate,
These planetary gears are directly connected to the input member and the output member, and in the speed increasing position, the rotation of the input member is transmitted to the ring gear of the second planetary gear and the sun gear of the third planetary gear via the first clutch. While releasing the third clutch,
The sun gear of the planetary gear of Id.
By transmitting the rotation of the input member to the first single planetary gear through the second clutch and releasing the sun gear of the first planetary gear by releasing the ring gear of the planetary gear of FIG. A gear mechanism for an automatic transmission, wherein the speed is increased exclusively by the first single planetary gear and power is transmitted to the output member. 4. A first brake that locks a carrier of a first planetary gear, a second brake that locks a sun gear of the first planetary gear, and a ring gear that locks a ring gear of a third planetary gear. The gear mechanism of the automatic transmission according to claim 3, comprising four brakes. 5. A fifth clutch is interposed between the output side of the second clutch and the sun gear of the first planetary gear, and the carrier of the first planetary gear is rotated in one direction via the first one-way clutch. A fourth clutch is disposed between the first brake and the carrier of the first planetary gear and the first one-way clutch, and the sun gear of the second planetary gear is connected via the third one-way clutch. A third brake that locks the rotation in one direction is provided, and a second one-way clutch is interposed between the sun gear of the first planetary gear and the sun gear of the second planetary gear. The gear mechanism of the automatic transmission according to claim 4, wherein a fourth one-way clutch is interposed between the ring gear and the fixed member.