KR100293664B1 - Automatic transmission of full shifting stage non-synchronous shifting two-simple type - Google Patents

Abstract

PURPOSE: An automatic transmission of full shifting stage non-synchronous shifting two-simple type is provided to make an automatic transmission of full shifting stage non-synchronous shifting two-simple type more efficient. CONSTITUTION: In automatic transmission of two-simple type, a first planetary carrier of a first planetary gear set(3) is directly connected with a second ring gear of a second planetary gear set(5) and a first ring gear of a first planetary gear set is directly connected with a second planetary carrier. The first planetary is connected parallel with a third brake(B3) and a third one-way clutch(O3). An input shaft(1) is selectively connected with a second power shaft(17) directly connected to a second sun gear by a third clutch(C3). The input shaft is connected parallel with a first power shaft(19) by a first clutch(C1) and a second one-way clutch(O2). The input shaft is connected with a third power shaft(23) by a second clutch(C2). The first power shaft is connected to a first brake(B1) with a first one-way clutch(O1) and connected with a second brake(B2).

Description

Full-speed asynchronous 2 simple automatic transmission

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a non-synchronous shifting two-simple type automatic transmission, which maintains a shifting feeling exhibited by the automatic transmission of the same type even when the position of the one-way clutch is changed and one clutch is deleted. At the same time, it's a full-speed, asynchronous two-simple automatic transmission that makes it smaller, lighter and less expensive to manufacture.

Composite planetary gearboxes for automatic transmissions include the Simpson, Ravigneaux and 2 simple models.

Among these composite planetary gears, 2 simple composite planetary gears are a combination of two single-pinion simple planetary gears, which are composed of the first ring gear, the second planetary carrier, and the first planetary carrier and the second ring gear. It realizes 1st speed and 2nd speed.

In general, an automatic transmission for a vehicle includes a transmission control unit (TCU) that automatically controls a transmission ratio in response to a change in a vehicle's driving speed and an engine load, thereby operating or inactivating a plurality of friction elements installed in a gear train. The rotational speed of the output stage is controlled by controlling any one of the three elements of the planetary gear set (sun gear, planet carrier, ring gear) as the input element and controlling the other element as the reaction force element.

On the other hand, the automatic transmission is easy to control by reducing the transmission shock even when only one element is activated or released without precisely coinciding the operating time of two actuating elements that are released or actuated when the gear is increased or decelerated (asynchronous shift). I am applying a one-way clutch to be able to do it.

FIG. 4 shows a configuration diagram of an automatic transmission power train of the two-simple combined planetary gear type system configured to apply a plurality of one-way clutches and brakes to perform asynchronous shifting at all shift stages. Indeed, this is the case with the General Motors 4T40-E automatic transmission.

As shown in FIG. 4, an example of the automatic transmission according to the prior art is a clutch employing method employing four clutches, three brakes and three one-way clutches based on two single planetary gear sets (hereinafter, ' Clutch hook-up system).

The automatic transmission according to the prior art receives the rotational power generated from the engine (E) from the torque converter to the input shaft (1) and then according to each shift stage the first planetary gear set (3) and the second planetary gear set (5) After shifting by various combinations of), and outputs through the second planetary carrier (CR2) of the second planetary gear set.

In the automatic transmission, the first planetary gear set 3 and the second planetary gear set 3, which are single-pinion planetary gear sets, have a first planetary carrier CR1 of the first planetary gear set by a fourth clutch C4. Optionally, the second ring gear R2 of the second planetary gear set 5 is connected, and the first ring gear R1 of the first planetary gear set 3 is connected to the second of the second planetary gear set 5. It is directly connected to the planet carrier CR2 and constitutes a gear train.

At this time, the first planet carrier CR1 is additionally connected in parallel with the third brake B3 and the third one-way clutch 03 installed in the transmission housing.

The input shaft 1 is connected to the second power shaft 17 directly connected to the second sun gear S2 via a third clutch C3 and a second one-way clutch 02 in parallel. The input shaft 1 is connected to the first power shaft 19 directly connected to the first sun gear S1 by the first clutch C1, and the input shafts connected to the two shafts 17 and 19 are simultaneously It is connected by the 3rd power shaft 23 and the 2nd clutch C2 which are directly connected to the 1st planet carrier CR1.

Meanwhile, the first power shaft 19 is connected to the first brake B1 which is fixed to the transmission housing and is connected to the first one-way clutch 01 in series and simultaneously to the second brake B2. It consists of a structure.

Referring to FIGS. 3 to 5, the shifting process at each shift stage with respect to the automatic transmission configured as described above is as follows.

First, when the shift lever (not shown) is selected as the forward D range and the opening amount of the throttle valve is increased, the transmission control unit operates the fourth clutch C4 to output the first speed shift ratio as shown in FIG. 5. .

Then, as can be seen in FIG. 4, the power is transmitted to the second sun gear S2 through the first power shaft 19 through the second one-way clutch 02, and accordingly, the second sun gear S2. Acts as an input element. At this time, the second ring gear (R2) of the second planetary gear set (5) is subjected to the reaction to reverse rotation, but the fourth clutch (C4) is in operation, the reverse rotational force is the third one-way clutch (03) Will be limited by Accordingly, the second ring gear R2 acts as a reaction force element.

Accordingly, as shown in the L1 diagram of FIG. 3, the second sun gear S2 is used as the input element, the second ring gear R2 is the reaction force element, and the second carrier CR2 is the output element. Therefore, the deceleration is made.

In this first speed state, the rotation of the first sun gear S1 becomes the reverse rotation, as shown in the L1 diagram.

For 1-> 2 shifting, the first brake B1 is operated in the 1-speed state.

Then, as can be seen in Figure 4, the first sun gear (S1) is limited to the reverse rotation by the first one-way clutch (01) connected to the first brake (B1), accordingly the first sun gear S1 acts as a reaction force element.

Thus, as shown in the lever diagram of Fig. 3, a shift state such as L2 is achieved. In addition, in the L2 state, since the rotation of the second ring gear R2 is in the forward direction, the third one-way clutch 03 connected to the second ring gear R2 by the fourth clutch C4 makes free rotation. Therefore, when the first brake B1 is operated during 1-> 2 shifting, the tie-up (synchronization fails) causes the friction element to over friction or engine stall due to a contradictory action between the friction elements. Phenomenon) Phenomenon does not occur.

By this action, since the first sun gear S1 acts as a reaction element, the reverse rotational force of the first planet carrier CR1 is further transmitted to the first ring gear R1 through the pinion gear 25 thereof. By further rotating the first ring gear R1, the first ring gear R1 is transferred to the second planet carrier CR2 integrally formed with the first ring gear R1 to output the second speed ratio.

For the 2-> 3 shift, the second clutch C2 is operated in the second speed state, that is, while the fourth clutch C4 and the first brake B1 are operated.

Then, the first planet carrier CR1 connected to the input shaft 1 by the second clutch C2 rotates at the same speed as the input shaft 1, and thus is driven by the second one-way clutch 02. It rotates at the same speed as the second sun gear S2. Therefore, this shift state becomes the L3 state of FIG. 3, and outputs the three-speed shift ratio.

At this time, since the first sun gear S1 and the second ring gear R2 are rotated forward, the first one-way clutch 01 and the third one-way clutch 03 are free to rotate.

For the 3-speed 4-speed shift, the second brake B2 is operated in the third speed state, that is, the second clutch C2, the fourth clutch C4, and the first brake B1 are operated.

When the second brake B2 is operated, the first sun gear S1 connected thereto is fixed to act as a reaction element, and the first planet carrier CR1 connected to the input shaft 1 by the second clutch C2 is input. Since it acts as an element, this shift state becomes a shift state such as L4 of FIG.

At this time, since the second sun gear S2 rotates faster than the rotation speed of the input shaft 1, the second one-way clutch 02 is in a free rotation state, and the second ring gear R2 is rotated forward, thereby being connected thereto. The third one-way clutch 03 is in a free rotation state. In addition, since the first power shaft 19 is fixed by the second brake B2, the first one-way clutch 01 connected thereto is in an inoperative state.

On the other hand, when the reverse R range is selected by the shift lever, the transmission control unit operates the first clutch C1 and the third brake B3.

Therefore, the first sun gear S1 connected to the input shaft 1 by the first clutch C1 acts as an input element, and the first planet carrier CR1 connected by the third brake B3 is fixed to the reaction element. Will act as. Therefore, this shift state becomes a shift state as shown in LR of FIG. 3, so that the second planet carrier CR2, which is an output element thereof, rotates in reverse.

At this time, since the first brake B1 does not operate, the first one-way clutch 01 is in an inoperative state, and the third one-way clutch 03 is operated by the third brake B3. Since the carrier CR1 is in a fixed state, the carrier CR1 is in an inoperative state.

However, although the second sun gear S2 is shown to rotate in reverse according to the LR diagram, since the fourth clutch C4 connected to the second ring gear R2 is released, the second sun gear S2 can rotate freely. The sun gear S2 is also free to rotate, so that the second one-way clutch 02 is not loaded.

By the above operation, when the automatic transmission according to the prior art is up-shifted to 1-2 stages, 2-3 stages and 3-4 stages, the 3,1,2 one-way clutch (03,01) , The asynchronous shift is made, and the third clutch C3 is operated to engage the engine brake in the "3" range, the "2" range, and the "1" range.

However, the above automatic transmission has a clutch hook-up system which is inefficiently constructed, and thus there is room for improvement in terms of manufacturing cost, weight and durability of the transmission.

Therefore, the present invention has been proposed to improve the above problems, and an object of the present invention is to change the position of some one-way clutch in the automatic transmission gear train, and propose a clutch hook-up system in which one clutch is deleted. The aim is to provide more efficient all-shift asynchronous two-simple automatic transmissions.

In order to achieve the above object, the present invention provides that the first planetary carrier of the first planetary gear set is directly connected to the second ring gear of the second planetary gear set, and the first ring gear of the first planetary gear set is the second planetary gear. A second planetary shaft directly connected to a second planetary carrier of the set, the first planetary carrier being connected in parallel with a third brake and a third one-way clutch installed in the transmission housing, the input shaft being directly connected to the second sun gear And a third clutch, the input shaft being connected in parallel by a first power shaft and a first clutch and a second one-way clutch, which are also directly connected to the first sun gear. It is connected by a third clutch and a second clutch directly connected to the planet carrier, the first power shaft is fixed to the transmission housing in series with the first one-way clutch It offers a full shift speed asynchronous simpeulhyeong automatic transmission 2 as the given connection and the first brake that are determined at the same time connected with the second brake.

1 is a power train configuration diagram of a full-speed asynchronous two-simple automatic transmission according to the present invention,

2 is a friction element operation table for each shift stage of the asynchronous 2-simple automatic transmission according to the present invention;

3 is a lever diagram of a full-speed asynchronous two-simple automatic transmission according to the present invention and the prior art,

4 is a power train configuration diagram of a full-speed asynchronous two-simple automatic transmission according to the prior art,

5 is a power train diagram of a conventional two-speed automatic two-speed automatic transmission according to the prior art.

Hereinafter, specific embodiments for realizing the above object will be described with reference to FIG. 1.

1 shows a configuration diagram of a power train for an automatic transmission according to the present invention.

Since the present invention is an improvement of the above automatic transmission, the two simple planetary gear sets, the power shaft for power transmission, and the arrangement of the brakes are the same, and the difference is the position of the one-way clutch and the number of clutches.

That is, in the first planetary gearset 3 and the second planetary gearset 5, the first planetary carrier CR1 of the first planetary gearset has a second ring gear R2 of the second planetary gearset 5. The first ring gear R1 of the first planetary gearset 3 constitutes a gear train directly connected to the second planetary carrier CR2 of the second planetary gearset 5.

On the other hand, the first planet carrier CR1 is connected in parallel with the third brake B3 and the third one-way clutch 03 provided in the transmission housing.

In addition, the input shaft 1 is selectively connected by the second power shaft 17 and the third clutch C3 directly connected to the second sun gear S2, and the input shaft 1 is the first sun gear S1. The input shaft (1) connected in parallel by the first power shaft (19), the first clutch (C1) and the second one-way clutch (03) directly connected to the two shafts (17, 19) ) Is also connected by a third power shaft 23 and a second clutch C2 directly connected to the first planet carrier CR1.

Meanwhile, the first power shaft 19 is connected to the first brake B1 fixed to the transmission housing via the first one-way clutch 01 and is connected to the second brake B2. have.

The difference in construction between the automatic transmission according to the present invention configured as described above and the automatic transmission according to the prior art is as follows.

That is, the fourth clutch C4 selectively connecting the first planet carrier CR1 and the second ring gear R2 is deleted and directly connected to each other, and between the input shaft 1 and the second power shaft 17. The second one-way clutch 02 formed is moved between the input shaft 1 and the first power shaft 19.

The shift process of the present invention configured as described above will be described with reference to FIGS. 1 to 3 as follows.

First, it should be noted that in the transmission according to the prior art, the fourth clutch C4 is continuously being operated during the forward shifting process. In the present invention, the fourth clutch C4 having such a function is deleted and directly connected to the fourth clutch C4. The fourth clutch C4 of the transmission according to the technology is in the same state as the operating state.

In addition, the second one-way clutch 02 of the third clutch C3 and the second one-way clutch 02 connected in parallel between the input shaft 1 and the second power shaft 17 in the transmission according to the prior art. ) And the third clutch C3 is operated throughout the entire shifting process except for the four-speed process in the forward shifting process, so that the third clutch C3 and the second one-way clutch 02 in the transmission according to the prior art The role is solved only by the third clutch C3.

First, for the first speed state, as shown in FIG. 2, the third clutch C3 is operated.

As shown in FIG. 1, the second sun gear S2 is driven by driving the second power shaft 17 connected to the input shaft 1 through the third clutch C3, and thus the second sun gear S2. Will act as an input element.

At this time, the second ring gear (R2) of the second planetary gear set 5 is subjected to a reaction force to reverse rotation, but the reverse rotational force is limited by the third one-way clutch 03, so that the second The ring gear R2 acts as a reaction force element.

Therefore, as in the first speed state of the transmission according to the prior art, the shift state corresponds to the L1 diagram in FIG. 3, and the second carrier CR2, which is an output element thereof, is output in a state in which it is decelerated with respect to the input.

In this first speed state, the rotation of the first sun gear S1 becomes the reverse rotation, as shown in the L1 diagram. Accordingly, the second one-way clutch 02 is in a free rotation state.

For the 1-> 2 shift, similarly to the shift of the transmission according to the prior art, the first brake B1 is operated in the first speed state, and accordingly the first one-way clutch 01 according to the same principle as the prior art description. Is operated so that the first sun gear S1 acts as a reaction force element, and thus a shift state as shown in L2 of FIG. 3 is achieved.

In addition, in the L2 state, since the rotation of the second ring gear R2 is in the forward direction, the third one-way clutch 03 is free to rotate. With regard to the second one-way clutch 02, the first power shaft 19 is in a stationary state, and thus becomes slower than the rotation speed of the input shaft 1, thereby becoming a free rotation state.

2-> 1 downshifting is performed by releasing the first brake B1 as opposed to the 1-> 2 shifting.

For the 2-> 3 shift, the second clutch C2 is operated in the second speed state, that is, while the third clutch C3 and the first brake B1 are operated.

Then, the first planet carrier CR1 connected to the input shaft 1 by the second clutch C2 rotates at the same speed as the input shaft 1, and therefore, the second driven by the third clutch C3. It rotates at the same speed as the sun gear S2. Therefore, this shift state becomes the L3 state of FIG. 3, and outputs the three speed shift ratio.

It should be noted here that once the third speed ratio is achieved, the third speed ratio is maintained even after the third clutch C3 is released.

That is, when the third clutch C3 is released, the second sun gear S2 may be freely rotated, and the second planetary carrier CR2, which is an output element, acts as a drag force by driving resistance. When the first planetary carrier CR1 connected to the clutch C2 is driven, the first planetary gear CR1 acts in a direction of increasing the rotation speed of the first sun gear S1.

At this time, the rotation speed of the first sun gear S1 by the second one-way clutch 02 exceeds the rotation speed of the first planet carrier CR1 connected by the input shaft 1 and the second clutch C2. You will not be able to.

Therefore, the rotational speed of the first sun gear S1 is maintained at the same speed as the rotational speed of the first planetary carrier CR1, and thus the speed ratio of the third speed is maintained.

That is, to summarize the 2-> 3 shifting process, when the third clutch is realized by operating the second clutch C2, the third clutch is released and accordingly, the second one-way clutch 02 is operated to maintain the third speed.

3-> 2 downshifting is contrary to the 2-> 3 shifting process, after releasing the load of the second one-way clutch 02 by operating the third clutch C3 before the shifting, the actual shifting is performed by the second clutch By releasing it.

For the 3-> 4 shifting, the second brake B2 is operated in the third speed state, that is, while the second clutch C2 and the first brake B1 are operated.

In this case, the first sun gear S1 acts as a reaction force element, and the first planet carrier CR1 acts as an input element, so that the shift state as shown in L4 of FIG. 3 is as described in the prior art description. It is a principle.

At this time, the first one-way clutch 01 is in an inoperative state because the first power shaft 19 is in a stopped state, and the second one-way clutch 02 is in a free rotation state, and the first planet carrier is an input element. The third one-way clutch 03 connected to the CR1 is also in a free rotation state.

On the other hand, when the reverse R range is selected by the shift lever, the transmission control unit operates the first clutch C1 and the third brake B3.

Therefore, the first sun gear S1 connected to the input shaft 1 by the first clutch C1 acts as an input element, and the first planet carrier CR1 connected by the third brake B3 is fixed to the reaction element. Will act as. Therefore, this shift state becomes a shift state as shown in LR of FIG. 3, so that the output of the second planet carrier CR2, which is the reverse element, is also reversed as described in the description of the prior art.

At this time, since the first brake B1 does not operate, the first one-way clutch 01 is in an inoperative state, and the second one-way clutch 02 has the first power shaft 19 and the input shaft 1 Since it rotates at the same speed, it is in an inoperative state, and the third one-way clutch 03 is in inoperative state because the first planet carrier CR1 is fixed by the operation of the third brake B3.

However, although the second sun gear S2 is shown to rotate in reverse according to the LR diagram, since the third clutch C3 connected thereto is released, the second sun gear S2 is free to rotate.

As shown in Fig. 2, in the third speed of the " 3 " range, the connection of the third clutch C3 is maintained without shifting after the shift, and the connection is maintained as described above. The engine brake is operated by the load torque transmitted from the CR2.

The first and second stages of the "3" range, the first and second stages of the "2" range, and the first stage of the "1" range are subjected to the same shifting procedures as those of the "D" stage, so descriptions are omitted. .

As can be seen from the above description, the full-speed asynchronous 2-simple automatic transmission according to the present invention changes the position of some one-way clutches in the conventional automatic transmission gear train and provides a clutch hook-up system in which one clutch is deleted. By reducing the clutch configuration while maintaining the same shifting feeling as the automatic transmission, it is possible to reduce the size and weight of the automatic transmission and to reduce the manufacturing cost, and to improve durability while being easy to assemble.

Claims (1)

In the two-simple automatic transmission combining two sets of single-pinion simple planetary gears, the first planetary carrier of the first planetary gear set is directly connected to the second ring gear of the second planetary gear set, and the first of the first planetary gearset. The ring gear is directly connected to the second planet carrier of the second planetary gear set, and the first planet carrier is connected in parallel with the third brake and the third one-way clutch installed in the transmission housing, and the input shaft is connected to the second sun gear. It is selectively connected by the second power shaft and the third clutch directly connected, the input shaft is also connected in parallel by the first power shaft and the first clutch and the second one-way clutch directly connected to the first sun gear. The input shaft is connected by a third clutch and a second clutch which are directly connected to the first planet carrier at the same time, and the first power shaft is a first brake fixed to the transmission housing. A first one-way clutch is coupled through a gear position also before asynchronous simpeulhyeong automatic transmission 2, it characterized in that the given connection and the second brake.

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