JP6869477B2 - Automatic transmission for vehicles - Google Patents

Description

The present invention relates to an automatic transmission of a vehicle.

Conventionally, for example, an automatic transmission for a vehicle disclosed in Patent Document 1 below has been known. This conventional automatic transmission for vehicles has four planetary mechanisms having a first element, a second element, and a third element, and a first engaging element, a second engaging element, a first clutch, a second clutch, and a first. It has six engaging elements, three clutches and a first brake. Then, in the conventional automatic transmission for vehicles, three engaging elements out of the six engaging elements are engaged to form a forward nine-speed stage and a reverse first-speed stage.

JP-A-2017-32026

In recent years, in order to improve the fuel efficiency of a vehicle, it has been actively proposed to increase the number of gears of the automatic transmission for a vehicle as in the conventional automatic transmission for a vehicle. In such a multi-speed shift, the gear ratio of each shift stage is set so that an efficient rotation speed range can be used when the engine or the like as a drive source generates a driving force. However, when widening the spread in the automatic transmission for vehicles for the purpose of further increasing the number of gears, it is generally necessary to change the gear ratio of each gear with respect to the widened spread. Therefore, the step ratio between the gear ratios may increase, and the increase in the step ratio may worsen the shift shock. Further, due to the change in the gear ratio, there is a possibility that an efficient rotation speed range for generating a driving force in the engine or the like cannot be used.

The present invention has been made to solve the above problems. That is, an object of the present invention is to provide an automatic transmission for a vehicle capable of suppressing deterioration of shift shock, widening the spread, and increasing the number of gears.

In order to solve the above problems, the invention of the automatic vehicle transmission according to claim 1 is arranged between an input shaft, an output shaft, and an input shaft and an output shaft, and has a first element and a second element. And the first planetary mechanism, the second planetary mechanism, the third planetary mechanism and the fourth planetary mechanism having the third element, the first clutch, the second clutch, the third clutch, the fourth clutch, the first brake, the second. The seven engaging elements of the brake and the third brake, the first connecting member that makes the first element of the first planetary mechanism and the fixing member in a disengageable connection state, and the second element and the first of the first planetary mechanism. (2) The second connecting member that connects the third element of the planetary mechanism to the connected state, the third connecting member that connects the third element of the first planetary mechanism and the input shaft, and the first element of the second planetary mechanism. The fourth connecting member that connects the first element of the third planetary mechanism and the first element of the third planetary mechanism, the fifth connecting member that connects the second element of the third planetary mechanism and the output shaft, and the third connecting member of the third planetary mechanism. The sixth connecting member that connects the three elements and the fixing member, the first element of the fourth planetary mechanism and the first element of the third planetary mechanism, or the first element and the third planetary of the fourth planetary mechanism. The third element of the mechanism is connected to the seventh connecting member, the second element of the fourth planetary mechanism and the input shaft, or the third element of the fourth planetary mechanism and the input shaft are connected to each other. The eighth connecting member, the third element and the output shaft of the fourth planetary mechanism, or the ninth connecting member for connecting the second element and the output shaft of the fourth planetary mechanism are provided. One brake allows the first element of the first planetary mechanism to be engaged and disengaged with respect to the fixed member, and the second brake allows the second element of the second planetary mechanism to be engaged and disengaged with respect to the fixed member, and the third brake. Allows the third element of the third planetary mechanism to be engaged and disengaged with respect to the fixing member, the first clutch engages the input shaft and the second element of the second planetary mechanism in a disengaged manner, and the second clutch , Two elements of the first element, the second element and the third element of the second planetary mechanism are detachably connected, and the third clutch is the third element of the fourth planetary mechanism and the eighth connecting member. And one of the ninth connecting members are detachably connected, and the fourth clutch is the first element of each of the first planetary mechanism, the second planetary mechanism, the third planetary mechanism and the fourth planetary mechanism. Two elements of the second element and the third element are detachably connected, and three of the seven engaging elements are engaged. It is composed of.

According to this, the spread can be widened without changing the gear ratio forming each shift stage in the automatic transmission for vehicles. As a result, the step ratio of the automatic transmission for the vehicle does not increase, and the shift shock at the time of shifting does not worsen. Therefore, in the automatic transmission for vehicles, extremely smooth shifting can be realized. Further, in the automatic transmission for vehicles, it is not necessary to change the gear ratio in order to widen the spread, so that when the engine as the driving source generates the driving force, an efficient engine speed range is used. be able to. As a result, the fuel efficiency of the vehicle is not deteriorated.

It is a skeleton figure which shows typically the automatic transmission for a vehicle in 1st Embodiment. It is a figure which shows the operating state of the clutch and the brake in each shift stage of the automatic transmission for vehicles of FIG. It is a speed diagram of the automatic transmission for vehicles of FIG. It is a skeleton figure which shows typically the 1st modification of 1st Embodiment. It is a skeleton figure which shows typically the 2nd modification of 1st Embodiment. It is a skeleton figure which shows typically the 3rd modification of 1st Embodiment. It is a skeleton figure which shows typically the 4th modification of 1st Embodiment. It is a skeleton figure which shows typically the 5th modification of 1st Embodiment. It is a skeleton figure which shows typically the 6th modification of 1st Embodiment. It is a skeleton figure which shows typically the 7th modification of 1st Embodiment. It is a skeleton figure which shows typically the 8th modification of 1st Embodiment. It is a skeleton figure which shows typically the 9th modification of 1st Embodiment. It is a skeleton figure which shows typically the automatic transmission for a vehicle in 2nd Embodiment. It is a figure which shows the operating state of the clutch and the brake in each shift stage of the automatic transmission for vehicles of FIG. It is a speed diagram of the automatic transmission for vehicles of FIG.

(First Embodiment)
Hereinafter, the first embodiment of the present invention will be described with reference to the drawings. In the drawings, the parts that are the same or equal to each other in each of the following embodiments and modifications are designated by the same reference numerals. Further, each figure used for explanation is a conceptual view, and the shape of each part may not always be exact.

As shown in FIG. 1, the vehicle automatic transmission 10 (hereinafter, also simply referred to as “device 10”) of the first embodiment includes an input shaft N and an output shaft T. The input shaft N and the output shaft T are rotatably supported around the axis L of the input shaft N with respect to the transmission case H as a fixing member. The input shaft N is a shaft member that inputs a rotational driving force from a power source (for example, an engine, an electric motor, etc.) via a clutch device (not shown) or the like. The output shaft T is a shaft member arranged coaxially with the input shaft N and outputting the changed rotational driving force to the drive wheels via a differential device (not shown) or the like.

Further, the device 10 has four single pinion type first planetary mechanisms P1, second planetary mechanisms P2, and first, which are sequentially arranged between the input shaft N and the output shaft T along the axis L of the input shaft N. The third planetary mechanism P3 and the fourth planetary mechanism P4 are provided. The first planetary mechanism P1, the second planetary mechanism P2, the third planetary mechanism P3, and the fourth planetary mechanism P4 are arranged side by side from the input shaft N toward the output shaft T in this order. Further, the device 10 has seven engaging elements of the first clutch CL1, the second clutch CL2, the third clutch CL3 and the fourth clutch CL4, and the first brake B1, the second brake B2 and the third brake B3. I have.

The first planetary mechanism P1 includes a first sun gear S1 as a first element rotatably supported coaxially with the axis L, a first ring gear R1 as a third element, and a first sun gear S1 and a first ring gear R1. It is composed of a first carrier C1 as a second element that rotatably supports the first pinion gear Q1 that meshes with. The second planetary mechanism P2 includes a second sun gear S2 as a third element rotatably supported coaxially with the axis L, a second ring gear R2 as a first element, and a second sun gear S2 and a second ring gear R2. It is composed of a second carrier C2 as a second element that rotatably supports the second pinion gear Q2 that meshes with. The third planetary mechanism P3 includes a third sun gear S3 as a first element rotatably supported coaxially with the axis L, a third ring gear R3 as a third element, and a third sun gear S3 and a third ring gear R3. It is composed of a third carrier C3 as a second element that rotatably supports the third pinion gear Q3 that meshes with. The fourth planetary mechanism P4 includes a fourth sun gear S4 as a first element rotatably supported coaxially with the axis L, a fourth ring gear R4 as a third element, and a fourth sun gear S4 and a fourth ring gear R4. It is composed of a fourth carrier C4 as a second element that rotatably supports the fourth pinion gear Q4 that meshes with.

The first clutch CL1 to the fourth clutch CL4 are engaging elements capable of selectively engaging and disengaging a plurality of elements. The first clutch CL1 to the fourth clutch CL4 are of a normally open type and are of a hydraulic type operated by the supplied hydraulic pressure. As a result, in the first clutch CL1 to the fourth clutch CL4, the hydraulic pressure is transferred from the hydraulic pump that operates based on the control command by the transmission ECU (TM-ECU) to the input shaft N and the oil passage formed in the transmission case H. When supplied, a plurality of clutch plates (not shown) are brought into contact with each other so that the driving force is transmitted between the target elements. Then, by separating the clutch plates from each other, the elements are separated from each other so that the driving force is not transmitted between the target elements.

As shown in FIG. 1, the first clutch CL1 connects the input shaft N and the second carrier C2 of the second planetary mechanism P2 in a disengageable manner. The second clutch CL2 integrally rotates the second planetary mechanism P2, and two elements of the second sun gear S2, the second ring gear R2, and the second carrier C2 of the second planetary mechanism P2 can be engaged and disengaged. To do. Specifically, in the present embodiment, as shown in FIG. 1, the second clutch CL2 connects the second sun gear S2 and the second carrier C2 in a disengageable manner. The third clutch CL3 is detachably connected to one of the eighth connecting member J8 and the ninth connecting member J9, which will be described later, and as shown in FIG. 1, the third carrier C3 of the third planetary mechanism P3 and the third clutch CL3 The output shaft T and the fourth ring gear R4 of the fourth planetary mechanism P4 are detachably connected to each other. The fourth clutch CL4 integrally rotates the first planetary mechanism P1 and enables two elements of the first sun gear S1, the first ring gear R1 and the first carrier C1 of the first planetary mechanism P1 to be engaged with each other. To do. Specifically, in the present embodiment, as shown in FIG. 1, the fourth clutch CL4 connects the first ring gear R1 and the first carrier C1 in a disengageable manner.

The first brake B1 to the third brake B3 are engaging elements provided in the transmission case H to brake the rotation of a predetermined element. The first brake B1 to the third brake B3 are of a hydraulic type operated by the supplied hydraulic pressure. As a result, when the first brake B1 to the third brake B3 are supplied with oil from a hydraulic pump that operates based on a control command by the TM-ECU through an oil passage formed in the transmission case H, a disc (not shown) is used. Presses the pad to brake the rotation of a given element of interest. Then, by separating the pad from the disc, rotation of a predetermined element is allowed.

As shown in FIG. 1, the first brake B1 enables the first sun gear S1 of the first planetary mechanism P1 to be engaged with and detached from the transmission case H. As shown in FIG. 1, the second brake B2 enables the second carrier C2 of the second planetary mechanism P2 to be engaged with and detached from the transmission case H. As shown in FIG. 1, the third brake B3 makes the third ring gear R3 of the third planetary mechanism P3 engageable and disengageable with respect to the transmission case H.

Further, in the device 10, as shown in FIG. 1, each element S1, S2, S3, S4, R1, R2, R3, R4, C1, C2 constituting the first planetary mechanism P1 to the fourth planetary mechanism P4, respectively. , C3, C4 are connected to any element of another planetary mechanism via any of the first connecting member J1 to the twelfth connecting member J12. Further, the first clutch CL1 to the fourth clutch CL4 are connected to any element of the first planetary mechanism P1 to the fourth planetary mechanism P4 via any of the first connecting members J1 to the eleventh connecting member J11. To. Further, the first brake B1 to the third brake B3 are connected to any element of the first planetary mechanism P1 to the fourth planetary mechanism P4 via any of the first connecting members J1 to the eleventh connecting member J11. To.

Specifically, as shown in FIG. 1, the first connecting member J1 brings the first sun gear S1 of the first planetary mechanism P1 into a connected state in which it can be engaged with and disengaged from the first brake B1 provided in the transmission case H. As shown in FIG. 1, the second connecting member J2 connects the first carrier C1 of the first planetary mechanism P1 and the second sun gear S2 of the second planetary mechanism P2. As shown in FIG. 1, the third connecting member J3 connects the first ring gear R1 of the first planetary mechanism P1 and the input shaft N.

As shown in FIG. 1, the fourth connecting member J4 connects the second ring gear R2 of the second planetary mechanism P2 and the third sun gear S3 of the third planetary mechanism P3. As shown in FIG. 1, the fifth connecting member J5 connects the third carrier C3 of the third planetary mechanism P3 and the output shaft T. As shown in FIG. 1, the sixth connecting member J6 brings the third ring gear R3 of the third planetary mechanism P3 into a connected state in which it can be engaged with and detached from the third brake B3 provided in the transmission case H. As shown in FIG. 1, the seventh connecting member J7 connects the third sun gear S3 of the third planetary mechanism P3 and the fourth sun gear S4 of the fourth planetary mechanism P4. As shown in FIG. 1, the eighth connecting member J8 connects the fourth carrier C4 of the fourth planetary mechanism P4 and the input shaft N.

As shown in FIG. 1, the ninth connecting member J9 connects the fourth ring gear R4 of the fourth planetary mechanism P4 to the output shaft T via the third clutch CL3 provided on the fifth connecting member J5. Put it in a state. As shown in FIG. 1, the tenth connecting member J10 connects the fourth clutch CL4 to the third connecting member J3. The eleventh connecting member J11 brings the second carrier C2 of the second planetary mechanism P2 into a connected state in which it can be engaged with and disengaged from the second brake B2 provided in the transmission case H. The twelfth connecting member J12 connects the fifth connecting member J5 and the output shaft T.

In the device 10 of the present embodiment configured as described above, the three engaging elements of the first clutch CL to the fourth clutch CL4 and the first brake B1 to the third brake B3 are engaged with each other. It is an automatic transmission device capable of forming a forward ten-speed reverse two-speed shift having reverse (High and Low), a 1st to 6th speed underdrive, and a 7th to 10th speed overdrive. Specifically, in the device 10, as shown in FIG. 2, when only the first brake B1, the second brake B2, and the third brake B3 are engaged, the rotation of the output shaft T with respect to the rotation of the input shaft N. Is reversed, and the vehicle is driven in reverse by reverse (Low). Further, when only the fourth clutch CL4 is engaged and only the second brake B2 and the third brake B3 are engaged, the rotation of the output shaft T is reversed with respect to the rotation of the input shaft N, and the reverse (Low) is performed. ), The vehicle is driven in reverse by reverse (High), which has a larger number of revolutions.

Further, in the device 10, as shown in FIG. 2, when only the second clutch CL2 is engaged and only the first brake B1 and the third brake B3 are engaged, the first clutch CL1 and the first clutch CL1 and the first clutch B3 are engaged. When only the second clutch CL2 is engaged and only the third brake B3 is engaged, the second speed is achieved. Further, when only the first clutch CL1 is engaged and only the first brake B1 and the third brake B3 are engaged, only the first clutch CL1 and the third clutch CL3 are engaged and the first clutch is engaged in the third speed. When only the three brakes B3 are engaged, the fourth speed is achieved. Further, when only the first clutch CL1 and the third clutch CL3 are engaged and only the first brake B1 is engaged, the first clutch CL1, the second clutch CL2 and the third clutch CL3 are engaged in the fifth speed. When it is done, it will be 6th speed.

Further, in the device 10, as shown in FIG. 2, when only the second clutch CL2 and the third clutch CL3 are engaged and only the first brake B1 is engaged, the second clutch CL2 and the second clutch CL2 and the second clutch B1 are engaged. When only the three clutches CL3 are engaged and only the second brake B2 is engaged, the speed becomes eight speed. Further, when only the third clutch CL3 is engaged and only the first brake B1 and the second brake B2 are engaged, only the third clutch CL3 and the fourth clutch CL4 are engaged and the second clutch is engaged in the ninth speed. When only the two brakes B2 are engaged, the speed becomes ten speed.

By the way, in the device 10, the ratio of the gear ratio on the Low side to the gear ratio on the High side (= (gear ratio on the Low side) / ( The spread that represents the gear ratio on the High side)) can be widened to increase the forward speed. Hereinafter, this will be specifically described with reference to the speed diagram shown in FIGS. 2 and 3. The speed diagram shown in FIG. 3 represents the speed ratio of the three elements of the first planetary mechanism P1 to the fourth planetary mechanism P4 in each shift stage, and each element of the first planetary mechanism P1 to the fourth planetary mechanism P4 is shown. The speed ratio is taken for each element in the vertical axis direction by arranging them at intervals (1: λ) corresponding to the gear ratio (λ) in the horizontal axis direction and the vertical axis direction. The speed line shown by the thick solid line in FIG. 3 indicates the speed line when the fourth clutch CL4 is in the engaged state.

When the device 10 (the same applies to the conventional automatic transmission for vehicles described above) forms the ninth speed, as shown in FIG. 3, the first ring gear R1 of the first planetary mechanism P1 is connected by the third connecting member J3. Rotation is input from the input shaft N (see FIG. 1), and the first sun gear S1 is fixed by the first brake B1. As a result, in the first planetary mechanism P1, the rotation speed of the first carrier C1 is created. Further, the first carrier C1 of the first planetary mechanism P1 and the second sun gear S2 of the second planetary mechanism P2 are connected by a second connecting member J2 (see FIG. 1), and the second of the second planetary mechanism P2. The carrier C2 is fixed by the second brake B2 via the eleventh connecting member J11. As a result, in the second planetary mechanism P2, the reverse rotation speed of the second ring gear R2 is created.

Further, the fourth carrier C4 of the fourth planetary mechanism P4 receives rotation from the input shaft N connected by the eighth connecting member J8 (see FIG. 1), and the fourth sun gear S4 and the fourth sun gear S4 of the fourth planetary mechanism P4 are input. (2) The second ring gear R2 of the planetary mechanism P2 is connected by the fourth connecting member J4 and the seventh connecting member J7 (see FIG. 1). As a result, in the fourth planetary mechanism P4, the rotation speed of the fourth ring gear R4 is created. The third sun gear S3 of the third planetary mechanism P3 and the second ring gear R2 of the second planetary mechanism P2 are connected by the fourth connecting member J4 (see FIG. 1), and the third carrier C3 and the third carrier C3 of the third planetary mechanism P3 are connected. The fourth ring gear R4 of the four planetary mechanism P4 is connected by the third clutch CL3 via the fifth connecting member J5 and the ninth connecting member J9. As a result, the rotation speed of the third carrier C3 of the third planetary mechanism P3 is created. At the time of forming the ninth speed, the third ring gear R3 of the third planetary mechanism P3 is not fixed by the third brake B3, so that it rotates freely. Since the third carrier C3 of the third planetary mechanism P3 is connected to the output shaft T via the fifth connecting member J5 and the twelfth connecting member J12, the rotation speed of the third carrier C3 is transmitted to the output shaft T. Will be done.

On the other hand, when the device 10 forms the tenth speed, as shown in FIGS. 2 and 3, the first sun gear S1 of the first planetary mechanism P1 is the first as compared with the case where the above-mentioned nine speed is formed. It differs in that it is not fixed by the brake B1. Further, when the device 10 forms the tenth speed, the first ring gear R1 and the first carrier C1 of the first planetary mechanism P1 pass through the tenth connecting member J10 as compared with the case of forming the ninth speed described above. It differs in that the first planetary mechanism P1 is integrally rotated by being connected by the clutch CL4.

As a result, as shown in FIG. 3, the rotation speed of the second sun gear S2 of the second planetary mechanism P2 increases and the reverse rotation speed of the second ring gear R2 of the second planetary mechanism P2 also increases as compared with the time of forming the nine speeds. To do. Similarly, the rotation speeds of the fourth sun gear S4 and the fourth ring gear R4 of the fourth planetary mechanism P4 and the third sun gear S3 and the third carrier C3 of the third planetary mechanism P3 also increased, and the rotation of the third carrier C3 increased. The number is transmitted to the output shaft T. This widens the spread in device 10, as shown in FIG.

Further, even when the device 10 forms a reverse (High), as shown in FIGS. 2 and 3, the first ring gear R1 and the first carrier C1 of the first planetary mechanism P1 pass through the tenth connecting member J10. It is connected by the fourth clutch CL4 and rotates integrally. Therefore, the increased rotation speed of the third carrier C3 is transmitted to the output shaft T, so that the device 10 can form a reverse (High).

As can be understood from the above description, the vehicle automatic transmission 10 of the above embodiment is arranged between the input shaft N, the output shaft T, and the input shaft N and the output shaft T, and is the first element. First sun gear S1, second ring gear R2, third sun gear S3 and fourth sun gear S4, first carrier C1, second carrier C2, third carrier C3 and fourth carrier C4, and second element. A first planetary mechanism P1, a second planetary mechanism P2, a third planetary mechanism P3, and a fourth planetary mechanism P4 having a first ring gear R1, a second sun gear S2, a third ring gear R3, and a fourth ring gear R4 as three elements, respectively. , The first clutch CL1, the second clutch CL2, the third clutch CL3, the fourth clutch CL4, the first brake B1, the second brake B2 and the third brake B3, and the first planetary mechanism P1. The first connecting member J1 that connects the one sun gear S1 and the transmission case H as a fixing member in a disengageable connection state, the first carrier C1 of the first planetary mechanism P1, and the second sun gear S2 of the second planetary mechanism P2. The second connecting member J2 that connects the first ring gear R1 of the first planetary mechanism P1 and the third connecting member J3 that connects the input shaft N, and the second ring gear R2 of the second planetary mechanism P2. A fourth connecting member J4 that connects the third sun gear S3 of the third planetary mechanism P3, and a fifth connecting member J5 that connects the third carrier C3 of the third planetary mechanism P3 and the output shaft T. The sixth connecting member J6 that connects the third ring gear R3 of the third planetary mechanism P3 and the transmission case H, the fourth sun gear S4 of the fourth planetary mechanism P4, and the third sun gear S3 of the third planetary mechanism P3 are connected. The seventh connecting member J7 to be connected, the eighth connecting member J8 to connect the fourth carrier C4 of the fourth planetary mechanism P4 and the input shaft N, the fourth ring gear R4 of the fourth planetary mechanism P4, and the output. A ninth connecting member J9 that connects the shaft T to the shaft T is provided, and the first brake B1 enables the first sun gear S1 of the first planetary mechanism P1 to be engaged and disengaged with respect to the transmission case H, and the second brake B2. Can engage and disengage the second carrier C2 of the second planetary mechanism P2 with respect to the transmission case H, and the third brake B3 can engage and disengage the third ring gear R3 of the third planetary mechanism P3 with respect to the transmission case H. And the first clutch C L1 connects the input shaft N and the second carrier C2 of the second planetary mechanism P2 in a disengageable manner, and the second clutch CL2 is the second sun gear S2, the second carrier C2 and the second carrier C2 of the second planetary mechanism P2. The second sun gear S2 and the second carrier C2, which are two elements of the ring gear R2, are detachably connected to each other, and the third clutch CL3 is the fourth ring gear R4 of the fourth planetary mechanism P4 and the eighth connecting member. The ninth connecting member J9, which is one of the J8 and the ninth connecting member J9, is detachably connected, and the fourth clutch CL4 has a first planetary mechanism P1, a second planetary mechanism P2, and a third planetary mechanism. The first sun gear S1, the second sun gear S2, the third sun gear S3 and the fourth sun gear, and the first carrier C1, the second carrier C2, the third carrier C3 and the fourth carrier C4, respectively, of P3 and the fourth planetary mechanism P4. And the first carrier C1 and the first ring gear R1 of the first planetary mechanism P1 which are two elements of the first ring gear R1, the second ring gear R2, the third ring gear R3 and the fourth ring gear R4 can be engaged and disengaged. It is configured to engage with and engage three of the seven engaging elements.

In this case, the first planetary mechanism P1, the second planetary mechanism P2, the third planetary mechanism P3, and the fourth planetary mechanism P4 are of the output shaft T from the side of the input shaft N along the axis L of the input shaft N. The first planetary mechanism P1, the second planetary mechanism P2, the third planetary mechanism P3, and the fourth planetary mechanism P4 are arranged in this order toward the side.

According to these, the spread can be widened without changing the gear ratio forming each shift stage in the vehicle automatic transmission 10. As a result, the step ratio of the automatic transmission device 10 for vehicles does not increase, and the shift shock at the time of shifting does not worsen. Therefore, in the automatic transmission device 10 for vehicles, extremely smooth shifting can be realized. Further, in the automatic transmission 10 for vehicles, since it is not necessary to change the gear ratio in order to widen the spread, when the engine as the driving source generates the driving force, an efficient engine speed range is used. can do. As a result, the fuel efficiency of the vehicle is not deteriorated.

Further, the fourth clutch CL4 is arranged along the axis L of the input shaft N in the order of the first planetary mechanism P1, the second planetary mechanism P2, the third planetary mechanism P3, and the fourth planetary mechanism P4. By connecting the first carrier C1 of the first sun gear S1, the first carrier C1 and the first ring gear R1 of the mechanism P1 and the first ring gear R1, the first planetary mechanism P1 can be rotated integrally. As a result, the spread of the automatic transmission device 10 for vehicles can be appropriately widened without being excessively widened, and an increase in the step ratio due to the increase in the number of gears can be suppressed.

Further, in this case, the first planetary mechanism P1, the second planetary mechanism P2, the third planetary mechanism P3, and the fourth planetary mechanism P4 can be configured only by the single pinion type planetary mechanism. Thereby, the structures of the first planetary mechanism P1, the second planetary mechanism P2, the third planetary mechanism P3, and the fourth planetary mechanism P4 can be simplified.

(First modification of the first embodiment)
Next, the configuration of the first modification of the first embodiment will be described with reference to FIG. 4, which is shown corresponding to FIG. Here, in the first modification, in the first planetary mechanism P1, the first sun gear S1 is the first element, the first carrier C1 is the second element, and the first ring gear R1 is the third element. Further, in the second planetary mechanism P2, the second sun gear S2 is the first element, the second carrier C2 is the second element, and the second ring gear R2 is the third element. Further, in the third planetary mechanism P3, the third sun gear S3 is the first element, the third carrier C3 is the second element, and the third ring gear R3 is the third element. Further, in the fourth planetary mechanism P4, the fourth sun gear S4 is the first element, the fourth carrier C4 is the second element, and the fourth ring gear R4 is the third element.

Therefore, in the vehicle automatic transmission 11 of the first modification, the first carrier C1 of the first planetary mechanism P1 is changed to be connected to the second ring gear R2 of the second planetary mechanism P2 by the second connecting member J2. In that respect, the configuration is different from that of the device 10. Further, in the vehicle automatic transmission 11, the device 10 is changed so that the second sun gear S2 of the second planetary mechanism P2 is connected to the third sun gear S3 of the third planetary mechanism P3 by the fourth connecting member J4. It has a different configuration from.

Also in the vehicle automatic transmission device 11 having such a configuration, as shown in FIG. 2, the first clutch CL1 to the fourth clutch CL4 and the first brake B1 to the third brakes B1 to the third, as in the device 10 of the first embodiment. By selectively engaging three of the seven engaging elements of the brake B3 to regulate the rotation of each element of the first planetary mechanism P1 to the fourth planetary mechanism P4, the forward ten-speed It is possible to form a gear and a reverse second gear.

(Second modification of the first embodiment)
Next, the configuration of the second modification of the first embodiment will be described with reference to FIG. 5, which is shown corresponding to FIG. Here, in the second modification, in the first planetary mechanism P1, the first sun gear S1 is the first element, the first carrier C1 is the second element, and the first ring gear R1 is the third element. Further, in the second planetary mechanism P2, the second sun gear S2 is the first element, the second carrier C2 is the second element, and the second ring gear R2 is the third element. Further, in the third planetary mechanism P3, the third sun gear S3 is the first element, the third carrier C3 is the second element, and the third ring gear R3 is the third element. Further, in the fourth planetary mechanism P4, the fourth sun gear S4 is the first element, the fourth carrier C4 is the second element, and the fourth ring gear R4 is the third element.

Therefore, in the vehicle automatic transmission 12 of the second modification, the first carrier C1 of the first planetary mechanism P1 is changed so as to be connected to the second ring gear R2 of the second planetary mechanism P2 by the second connecting member J2. In that respect, the configuration is different from that of the device 10. Further, in the vehicle automatic transmission 12, the device 10 is changed so that the second sun gear S2 of the second planetary mechanism P2 is connected to the third sun gear S3 of the third planetary mechanism P3 by the fourth connecting member J4. It has a different configuration from. Further, in the vehicle automatic transmission 12, the fourth ring gear R4 of the fourth planetary mechanism P4 is connected to the fifth connecting member J5 and the twelfth connecting member J12, that is, the output shaft T by the ninth connecting member J9. The configuration is different from that of the device 10 in that it is changed.

Further, in the vehicle automatic transmission 12, the second clutch CL2 is changed so that the second carrier C2 of the second planetary mechanism P2 and the second ring gear R2 of the second planetary mechanism P2 are detachably connected to each other. The configuration is different from that of the device 10. Further, in the automatic transmission device 12 for vehicles, the third clutch CL3 is changed to connect the fourth carrier C4 of the fourth planetary mechanism P4 and the input shaft N so as to be detachably connected via the eighth connecting member J8. In that respect, the configuration is different from that of the device 10.

In the vehicle automatic transmission device 12 having such a configuration, as in the device 10 of the first embodiment, as shown in FIG. 2, the first clutch CL1 to the fourth clutch CL4 and the first brake B1 to the third brake B1 to the third. By selectively engaging three of the seven engaging elements of the brake B3 to regulate the rotation of each element of the first planetary mechanism P1 to the fourth planetary mechanism P4, the forward ten-speed It is possible to form a gear and a reverse second gear.

(Third variant of the first embodiment)
Next, the configuration of the third modification of the first embodiment will be described with reference to FIG. 6, which is shown corresponding to FIG. The vehicle automatic transmission 13 of the third modification has a configuration different from that of the device 10 in that the first planetary mechanism P1 is changed to a double pinion type. Therefore, in the third modification, in the first planetary mechanism P1, the first sun gear S1 is the first element, the first ring gear R1 is the second element, and the first carrier C1 is the third element. Further, in the second planetary mechanism P2, the second sun gear S2 is the first element, the second carrier C2 is the second element, and the second ring gear R2 is the third element. Further, in the third planetary mechanism P3, the third sun gear S3 is the first element, the third carrier C3 is the second element, and the third ring gear R3 is the third element. Further, in the fourth planetary mechanism P4, the fourth sun gear S4 is the first element, the fourth carrier C4 is the second element, and the fourth ring gear R4 is the third element.

Therefore, in the vehicle automatic transmission 13, the device 10 is changed so that the first ring gear R1 of the first planetary mechanism P1 is connected to the second ring gear R2 of the second planetary mechanism P2 by the second connecting member J2. It has a different configuration from. Further, the vehicle automatic transmission 13 has a configuration different from that of the device 10 in that the first carrier C1 of the first planetary mechanism P1 is changed so as to be connected by the input shaft N and the third connecting member J3. .. Further, in the vehicle automatic transmission 13, the device 10 is changed so that the second sun gear S2 of the second planetary mechanism P2 is connected to the third sun gear S3 of the third planetary mechanism P3 by the fourth connecting member J4. It has a different configuration from.

Further, in the vehicle automatic transmission 13, the first clutch CL1 is changed so that the first carrier C1 of the first planetary mechanism P1 and the second carrier C2 of the second planetary mechanism P2 are detachably connected to each other. The configuration is different from that of the device 10. Further, in the vehicle automatic transmission 13, the second clutch CL2 is changed so that the second sun gear S2 of the second planetary mechanism P2 and the second ring gear R2 of the second planetary mechanism P2 are detachably connected to each other. The configuration is different from that of the device 10. Further, in the vehicle automatic transmission 13, the third clutch CL3 passes through the fourth connecting member J4 and the seventh connecting member J7, and the second sun gear S2 of the second planetary mechanism P2 and the fourth of the fourth planetary mechanism P4. The configuration is different from that of the device 10 in that the sun gear S4 is changed so as to be connected to the sun gear S4 so as to be detachably connected.

In the vehicle automatic transmission device 13 having such a configuration, as in the device 10 of the first embodiment, as shown in FIG. 2, the first clutch CL1 to the fourth clutch CL4 and the first brake B1 to the third brake B1 to the third. By selectively engaging three of the seven engaging elements of the brake B3 to regulate the rotation of each element of the first planetary mechanism P1 to the fourth planetary mechanism P4, the forward ten-speed It is possible to form a gear and a reverse second gear.

(Fourth variant of the first embodiment)
Next, the configuration of the fourth modification of the first embodiment will be described with reference to FIG. 7, which is shown corresponding to FIG. The vehicle automatic transmission 14 of the fourth modification has a configuration different from that of the device 10 in that the second planetary mechanism P2 is changed to a double pinion type in addition to the first planetary mechanism P1. Therefore, in the third modification, in the first planetary mechanism P1, the first sun gear S1 is the first element, the first ring gear R1 is the second element, and the first carrier C1 is the third element. Further, in the second planetary mechanism P2, the second sun gear S2 is the first element, the second ring gear R2 is the second element, and the second carrier C2 is the third element. Further, in the third planetary mechanism P3, the third sun gear S3 is the first element, the third carrier C3 is the second element, and the third ring gear R3 is the third element. Further, in the fourth planetary mechanism P4, the fourth sun gear S4 is the first element, the fourth carrier C4 is the second element, and the fourth ring gear R4 is the third element.

Therefore, in the vehicle automatic transmission 14, the device 10 is changed so that the first ring gear R1 of the first planetary mechanism P1 is connected to the second carrier C2 of the second planetary mechanism P2 by the second connecting member J2. It has a different configuration from. Further, in the vehicle automatic transmission 14, the device 10 is changed so that the second sun gear S2 of the second planetary mechanism P2 is connected to the third sun gear S3 of the third planetary mechanism P3 by the fourth connecting member J4. It has a different configuration from.

Further, in the vehicle automatic transmission 14, the input shaft N in which the first clutch CL1 is connected to the first carrier C1 of the first planetary mechanism P1 via the third connecting member J3 and the second of the second planetary mechanism P2. The configuration is different from that of the device 10 in that the ring gear R2 is changed so as to be connected to the ring gear R2 so as to be detachably connected. Further, the vehicle automatic transmission 14 is different from the device 10 in that the second brake B2 is changed to brake the rotation of the second ring gear R2 of the second planetary mechanism P2 via the eleventh connecting member J11. It is composed.

In the vehicle automatic transmission device 14 having such a configuration, as in the device 10 of the first embodiment, as shown in FIG. 2, the first clutch CL1 to the fourth clutch CL4 and the first brake B1 to the third brake B1 to the third. By selectively engaging three of the seven engaging elements of the brake B3 to regulate the rotation of each element of the first planetary mechanism P1 to the fourth planetary mechanism P4, the forward ten-speed It is possible to form a gear and a reverse second gear.

(Fifth variant of the first embodiment)
Next, the configuration of the fifth modification of the first embodiment will be described with reference to FIG. 8 shown in correspondence with FIG. Here, in the fifth modification, in the first planetary mechanism P1, the first sun gear S1 is the first element, the first carrier C1 is the second element, and the first ring gear R1 is the third element. Further, in the second planetary mechanism P2, the second sun gear S2 is the first element, the second carrier C2 is the second element, and the second ring gear R2 is the third element. Further, in the third planetary mechanism P3, the third sun gear S3 is the first element, the third carrier C3 is the second element, and the third ring gear R3 is the third element. Further, in the fourth planetary mechanism P4, the fourth sun gear S4 is the first element, the fourth carrier C4 is the second element, and the fourth ring gear R4 is the third element.

Therefore, in the vehicle automatic transmission 15 (hereinafter, also simply referred to as “device 15”) of the fifth modification, the third carrier C3 of the third planetary mechanism P3 is the fourth carrier C4 of the fourth planetary mechanism P4. The configuration is different from that of the device 10 in that it is changed so as to be connected by the fifth connecting member J5. Further, the device 15 has a different configuration from the device 10 in that the third ring gear R3 of the third planetary mechanism P3 is changed so as to be connected by the fourth sun gear S4 of the fourth planetary mechanism P4 and the seventh connecting member J7. It has become. Further, the device 15 has a different configuration from the device 10 in that the first carrier C1 of the first planetary mechanism P1 is connected to the second ring gear R2 of the second planetary mechanism P2 by the second connecting member J2. It has become. Further, the device 15 has a different configuration from the device 10 in that the second sun gear S2 of the second planetary mechanism P2 is connected to the third sun gear S3 of the third planetary mechanism P3 by the fourth connecting member J4. It has become.

Further, in the device 15, the device 10 is changed so that the third clutch CL3 connects the fourth ring gear R4 of the fourth planetary mechanism P4 and the input shaft N via the eighth connecting member J8 so as to be detachably connected. It has a different configuration from.

In the device 15 having such a configuration, as in the device 10 of the first embodiment, as shown in FIG. 2, the first clutch CL1 to the fourth clutch CL4 and the first brake B1 to the third brake B3 are seven. By selectively engaging three of the three engaging elements to regulate the rotation of each element of the first planetary mechanism P1 to the fourth planetary mechanism P4, the forward ten-speed stage and the reverse two A speed change gear can be formed.

(Sixth variant of the first embodiment)
Next, the configuration of the sixth modification of the first embodiment will be described with reference to FIG. 9, which is shown in correspondence with FIG. The vehicle automatic transmission 16 of the sixth modification has a configuration different from that of the device 15 in that the output shaft T is changed so as to extend in a direction orthogonal to the axis L of the input shaft N. Further, in the vehicle automatic transmission 16, the fourth planetary mechanism P4 is rotatably provided around the axis L of the input shaft N on the outer peripheral side of the third planetary mechanism P3, that is, on the axis L of the input shaft N. The configuration is different from that of the device 15 in that it is changed so as to be at a right angle. Further, in the vehicle automatic transmission 16, the fourth sun gear S4 of the single pinion type fourth planetary mechanism P4 is integrally arranged on the outer peripheral side of the third ring gear R3 of the single pinion type third planetary mechanism P3. As a result, the configuration is different from that of the device 15 in that the seventh connecting member J7 is formed. Further, in the automatic transmission 16 for vehicles, the ninth connecting member J9 connects the fourth carrier C4 of the fourth planetary mechanism P4 and the third carrier C3 of the third planetary mechanism P3, and the third carrier C3 of the third planetary mechanism P3 is connected. The configuration is different from that of the device 15 in that it is changed so as to be connected to the fifth connecting member J5 via the three carriers C3.

Further, in the vehicle automatic transmission 16, the second clutch CL2 can engage and disengage the second ring gear R2 of the second planetary mechanism P2 and the second carrier C2 of the second planetary mechanism P2 via the second connecting member J2. The configuration is different from that of the device 15 in that it is changed so as to be connected to the device 15.

In the vehicle automatic transmission 16 having such a configuration, as in the device 10 of the first embodiment (device 15 of the fifth modification), as shown in FIG. 2, the first clutch CL1 to the fourth clutch CL4, And, by selectively engaging three of the seven engaging elements of the first brake B1 to the third brake B3, the rotation of each element of the first planetary mechanism P1 to the fourth planetary mechanism P4. By regulating the above, it is possible to form a forward ten-speed gear and a reverse two-speed gear. The vehicle automatic transmission 16 can be configured as an automatic transmission for front wheel drive (FF) by providing the fourth planetary mechanism P4 at a right angle to the axis L of the input shaft N. ..

(Seventh variant of the first embodiment)
Next, the configuration of the seventh modification of the first embodiment will be described with reference to FIG. 10, which is shown in correspondence with FIG. Here, in the seventh modification, in the first planetary mechanism P1, the first sun gear S1 is the first element, the first carrier C1 is the second element, and the first ring gear R1 is the third element. Further, in the second planetary mechanism P2, the second ring gear R2 is the first element, the second carrier C2 is the second element, and the second sun gear S2 is the third element. Further, in the third planetary mechanism P3, the third sun gear S3 is the first element, the third carrier C3 is the second element, and the third ring gear R3 is the third element. Further, in the fourth planetary mechanism P4, the fourth sun gear S4 is the first element, the fourth carrier C4 is the second element, and the fourth ring gear R4 is the third element.

Therefore, in the vehicle automatic transmission 17 of the seventh modification, the second sun gear S2 of the second planetary mechanism P2 is changed so as to be connected to the first carrier C1 of the first planetary mechanism P1 and the second connecting member J2. In that respect, the configuration is different from that of the device 15. Further, in the vehicle automatic transmission 17, the device 15 is changed so that the second ring gear R2 of the second planetary mechanism P2 is connected to the third sun gear S3 of the third planetary mechanism P3 by the fourth connecting member J4. It has a different configuration from.

In the vehicle automatic transmission device 17 having such a configuration, as shown in FIG. 2, the first clutch CL1 to the fourth clutch CL4, as in the device 10 of the first embodiment (device 15 of the fifth modification). And, by selectively engaging three of the seven engaging elements of the first brake B1 to the third brake B3, the rotation of each element of the first planetary mechanism P1 to the fourth planetary mechanism P4. By regulating the above, it is possible to form a forward ten-speed gear and a reverse two-speed gear.

In addition, also in the vehicle automatic transmissions 15, 16 and 17 in the fifth modification, the sixth modification and the seventh modification of the first embodiment, for example, as shown in FIGS. 6 and 7. The one planetary mechanism P1 can be changed to a double pinion type, and the second planetary mechanism P2 can be changed to a double pinion type.

(Eighth variant of the first embodiment)
Next, the configuration of the eighth modification of the first embodiment will be described with reference to FIG. 11, which shows a part corresponding to FIG. In the vehicle automatic transmission 18 of the eighth modification, the fourth clutch CL4 is detachably connected to the first sun gear S1 of the first planetary mechanism P1 and the first carrier C1 of the first planetary mechanism P1. The configuration is different from that of the device 10 in that it is changed as described above.

Even in the vehicle automatic transmission 18 having such a configuration, the first sun gear S1 of the first planetary mechanism P1 and the first carrier C1 of the first planetary mechanism P1 are connected by the fourth clutch CL4. The first sun gear S1, the first ring gear R1 and the first carrier C1 of the planetary mechanism P1 can be rotated integrally. Therefore, in the vehicle automatic transmission device 18, as in the device 10 of the first embodiment, as shown in FIG. 2, the first clutch CL1 to the fourth clutch CL4 and the first brake B1 to the third brake B3 By selectively engaging three of the seven engaging elements to regulate the rotation of each element of the first planetary mechanism P1 to the fourth planetary mechanism P4, the forward ten-speed stage and the reverse A second gear can be formed.

(Ninth variant of the first embodiment)
Next, the configuration of the ninth modification of the first embodiment will be described with reference to FIG. 12, which shows a part corresponding to FIG. In the vehicle automatic transmission 19 of the ninth modification, the fourth clutch CL4 is detachably connected to the first sun gear S1 of the first planetary mechanism P1 and the first ring gear R1 of the first planetary mechanism P1. The configuration is different from that of the device 10 in that it is changed as described above.

Even in the vehicle automatic transmission 19 having such a configuration, the first sun gear S1 of the first planetary mechanism P1 and the first ring gear R1 of the first planetary mechanism P1 are connected by the fourth clutch CL4. The first sun gear S1, the first ring gear R1 and the first carrier C1 of the planetary mechanism P1 can be rotated integrally. Therefore, in the vehicle automatic transmission device 19, as in the device 10 of the first embodiment, as shown in FIG. 2, the first clutch CL1 to the fourth clutch CL4 and the first brake B1 to the third brake B3 By selectively engaging three of the seven engaging elements to regulate the rotation of each element of the first planetary mechanism P1 to the fourth planetary mechanism P4, the forward ten-speed stage and the reverse A second gear can be formed.

(Second Embodiment)
Next, the second embodiment of the present invention will be described. In the vehicle automatic transmission 20 of the second embodiment (hereinafter, also simply referred to as "device 20"), as shown in FIG. 13, the first planetary mechanism P1 and the second planetary mechanism P2 are changed to a double pinion type. In that respect, the configuration is different from that of the device 10 of the first embodiment shown in FIG. Further, in the device 20, the first ring gear R1 (second element) of the first planetary mechanism P1 is connected to the second carrier C2 (third element) of the second planetary mechanism P2 by the second connecting member J2. It has a different configuration from the device 10 in that it has been changed. Further, in the device 20, the second sun gear S2 (first element) of the second planetary mechanism P2 is connected to the third sun gear S3 (first element) of the third planetary mechanism P3 by the fourth connecting member J4. The configuration is different from that of the device 10 in that it is changed.

Further, in the device 20, the first clutch CL1 is connected to the first carrier C1 (third element) of the first planetary mechanism P1 via the third connecting member J3, and the input shaft N and the second planetary mechanism P2 are connected. The configuration is different from that of the device 10 in that the two ring gear R2 (second element) is changed so as to be engaged and disengaged. Further, also in the device 20, the second clutch CL2 connects the second sun gear S2 of the second planetary mechanism P2 and the second carrier C2 of the second planetary mechanism P2 in a disengageable manner. Further, the vehicle automatic transmission 20 is different from the device 10 in that the second brake B2 is changed to brake the rotation of the second ring gear R2 of the second planetary mechanism P2 via the eleventh connecting member J11. It is composed.

Further, in the device 20, the fourth clutch CL4 is changed so as to connect the second carrier C2 of the second planetary mechanism P2 and the third carrier C3 of the third planetary mechanism P3 so as to be detachably connected to the device 10. It's different.

In the device 20 of the second embodiment configured as described above, the three engaging elements of the first clutch CL to the fourth clutch CL4 and the first brake B1 to the third brake B3 are engaged with each other. , Reverse, 1st to 8th speed underdrive, and 9th to 12th speed overdrive, which is an automatic transmission capable of forming 12 forward speeds and 1 reverse speed. Specifically, in the device 20, as shown in FIG. 14, when only the first brake B1, the second brake B2, and the third brake B3 are engaged, the rotation of the output shaft T with respect to the rotation of the input shaft N. Is reversed, and the vehicle is driven in reverse by reverse.

Further, in the device 20, as shown in FIG. 14, when only the second clutch CL2 is engaged and only the first brake B1 and the third brake B3 are engaged, the first clutch CL1 and the first clutch CL1 and the first clutch B3 are engaged. When only the second clutch CL2 is engaged and only the third brake B3 is engaged, the second speed is achieved. Further, when only the first clutch CL1 is engaged and only the first brake B1 and the third brake B3 are engaged, only the first clutch CL1 and the fourth clutch CL4 are engaged and the first clutch CL4 is engaged in the third speed. When only the three brakes B3 are engaged, the fourth speed is achieved. Further, when only the third clutch CL3 and the fourth clutch CL4 are engaged and only the third brake B3 is engaged, only the third clutch CL3 and the fourth clutch CL4 are engaged and the third brake B3 is engaged. When only one brake B1 is engaged, it becomes the sixth speed. Further, when only the first clutch CL1 and the third clutch CL3 are engaged and only the first brake B1 is engaged, the first clutch CL1, the second clutch CL2 and the third clutch CL3 are engaged in the seventh speed. When it is done, it will be 8th speed.

Further, in the device 20, as shown in FIG. 14, when only the second clutch CL2 and the third clutch CL3 are engaged and only the first brake B1 is engaged, the second clutch CL2 and the second clutch CL2 and the second clutch are engaged. When only the three clutches CL3 are engaged and only the second brake B2 is engaged, the speed becomes ten speed. Further, when only the third clutch CL3 is engaged and only the first brake B1 and the second brake B2 are engaged, only the third clutch CL3 and the fourth clutch CL4 are engaged at the eleventh speed. When only the second brake B2 is engaged, the 12th speed is achieved.

By the way, also in the device 20 of the second embodiment, the ratio of the gear ratio on the Low side to the gear ratio on the High side (= (Low side) without changing each gear ratio in the conventional automatic transmission for vehicles described above. (Gear ratio on the High side) / (Gear ratio on the High side))) can be widened to increase the forward twelve speeds. Hereinafter, this will be specifically described with reference to the speed diagrams shown in FIGS. 14 and 15. The speed diagram shown in FIG. 15 represents the speed ratio of the three elements of the first planetary mechanism P1 to the fourth planetary mechanism P4 in each shift stage, and each element of the first planetary mechanism P1 to the fourth planetary mechanism P4 is shown. The speed ratio is taken for each element in the vertical axis direction by arranging them at intervals (1: λ) corresponding to the gear ratio (λ) in the horizontal axis direction and the vertical axis direction. The speed line shown by the thick solid line in FIG. 15 indicates the speed line when the fourth clutch CL4 is in the engaged state.

When the device 20 forms the eleventh speed, as shown in FIG. 15, the first carrier C1 of the first planetary mechanism P1 is rotated from the input shaft N (see FIG. 13) connected by the third connecting member J3. Input, the first sun gear S1 is fixed by the first brake B1. As a result, in the first planetary mechanism P1, the rotation speed of the first ring gear R1 is created. Further, the first ring gear R1 of the first planetary mechanism P1 and the second carrier C2 of the second planetary mechanism P2 are connected by a second connecting member J2 (see FIG. 13), and the second of the second planetary mechanism P2. The ring gear R2 is fixed by the second brake B2 via the eleventh connecting member J11. As a result, in the second planetary mechanism P2, the reverse rotation speed of the second sun gear S2 is created.

Further, the fourth carrier C4 of the fourth planetary mechanism P4 receives rotation from the input shaft N connected by the eighth connecting member J8 (see FIG. 13), and the fourth sun gear S4 and the fourth sun gear S4 of the fourth planetary mechanism P4 are input. The second sun gear S2 of the two planetary mechanism P2 is connected by the fourth connecting member J4 and the seventh connecting member J7 (see FIG. 13). As a result, in the fourth planetary mechanism P4, the rotation speed of the fourth ring gear R4 is created. The third sun gear S3 of the third planetary mechanism P3 and the second ring gear R2 of the second planetary mechanism P2 are connected by the fourth connecting member J4 (see FIG. 13), and the third carrier C3 and the third carrier C3 of the third planetary mechanism P3 are connected. (4) The fourth ring gear R4 of the planetary mechanism P4 is connected by the third clutch CL3 via the fifth connecting member J5 and the ninth connecting member J9 (see FIG. 13). As a result, the rotation speed of the third carrier C3 of the third planetary mechanism P3 is created. At the time of forming the eleventh speed, the third ring gear R3 of the third planetary mechanism P3 is not fixed by the third brake B3, so that it rotates freely. Since the third carrier C3 of the third planetary mechanism P3 is connected to the output shaft T via the fifth connecting member J5 and the twelfth connecting member J12, the rotation speed of the third carrier C3 is transmitted to the output shaft T. Will be done.

On the other hand, when the device 20 forms the twelve speeds, as shown in FIGS. 14 and 15, the first sun gear S1 of the first planetary mechanism P1 is compared with the case where the eleventh speed is formed. It differs in that it is not fixed by the first brake B1. Further, when the device 20 forms the twelve speeds, the second carrier C2 (third element) of the second planetary mechanism P2 and the third carrier of the third planetary mechanism P3 are compared with the case of forming the eleventh speed described above. It differs from C3 (second element) in that it is connected by the fourth clutch CL4 via the tenth connecting member J10 and rotates integrally.

When the twelve speeds are formed in the device 20, the second sun gear S2 of the second planetary mechanism P2 and the fourth sun gear S4 of the fourth planetary mechanism P4 are connected by the fourth connecting member J4 and the seventh connecting member J7. (See FIG. 13). Further, in the device 20, the third carrier C3 of the third planetary mechanism P3 and the second planetary mechanism connected by the third clutch CL3 to the fourth ring gear R4 of the fourth planetary mechanism P4 via the fifth connecting member J5. The second carrier C2 of P2 is connected by the fourth clutch CL4 via the tenth connecting member J10 (see FIG. 13). Further, in the device 20, the fourth sun gear S4 of the fourth planetary mechanism P4 and the third sun gear S3 of the third planetary mechanism P3 are connected by the seventh connecting member J7 (see FIG. 13). Further, rotation from the input shaft N is input to the fourth carrier C4 of the fourth planetary mechanism P4 via the eighth connecting member J8 (see FIG. 13). As a result, in the device 20, the second sun gear S2 and the second carrier C2 of the second planetary mechanism P2, and the fourth sun gear S4 and the fourth ring gear R4 of the fourth planetary mechanism P4 when forming the twelve speeds are formed. The number of revolutions is made.

As a result, the rotation speed of the third carrier C3 of the third planetary mechanism P3 connected to the fourth ring gear R4 of the fourth planetary mechanism P4 by the third clutch CL3 is created. Since the third carrier C3 is connected to the output shaft T via the fifth connecting member J5 and the twelfth connecting member J12, the rotation speed of the third carrier C3 is transmitted to the output shaft T (FIG. See 13). Here, in the device 20, when the twelve speeds are formed, the second carrier C2 of the second planetary mechanism P2 and the fourth ring gear R4 of the fourth planetary mechanism P4 are caused by the third clutch CL3 and the fourth clutch CL4. Connected, the second carrier C2 and the fourth ring gear R4 rotate at the same speed. Therefore, when the 12th speed is formed, the rotation speed of the 4th ring gear R4 of the 4th planetary mechanism P4 is higher than that at the time of forming the 11th speed, so that the rotation speed of the 3rd carrier C3 of the 3rd planetary mechanism P3 is increased. Will also grow. This widens the spread in device 20, as shown in FIG.

As can be understood from the above description, in the vehicle automatic transmission 20 of the second embodiment, the first planetary mechanism P1 and the second planetary mechanism P2 are double pinion type planetary mechanisms, and the third planetary mechanism. P3 and the fourth planetary mechanism P4 are single pinion type planetary mechanisms, the first element of the first planetary mechanism P1, the first element of the second planetary mechanism P2, the first element and the fourth of the third planetary mechanism P3. The first elements of the planetary mechanism P4 are the first sun gear S1, the second sun gear S2, the third sun gear S3 and the fourth sun gear S4, respectively, and the third element of the first planetary mechanism P1 and the second element of the second planetary mechanism P2. The three elements, the second element of the third planetary mechanism P3 and the second element of the fourth planetary mechanism P4 are the first carrier C1, the second carrier C2, the third carrier C3 and the fourth carrier C4, respectively, and the first The second element of the planetary mechanism P1, the second element of the second planetary mechanism P2, the third element of the third planetary mechanism P3, and the third element of the fourth planetary mechanism P4 are the first ring gear R1 and the second ring gear R2, respectively. , The third ring gear R3 and the fourth ring gear R4, and the fourth clutch CL4 is the second carrier C2 which is the third element of the second planetary mechanism P2 and the third carrier C3 which is the second element of the third planetary mechanism P3. And are connected in a detachable manner.

According to this, the spread can be widened without changing the gear ratio forming each shift stage in the vehicle automatic transmission 20. As a result, the step ratio of the vehicle automatic transmission 20 does not increase, and the shift shock at the time of shifting does not worsen. Therefore, in the automatic transmission device 20 for a vehicle, extremely smooth shifting can be realized. Further, in the automatic transmission 20 for vehicles, since it is not necessary to change the gear ratio in order to widen the spread, when the engine as the driving source generates the driving force, an efficient engine speed range is used. can do. As a result, the fuel efficiency of the vehicle is not deteriorated.

The implementation of the present invention is not limited to the above-described embodiments and the above-mentioned modifications, and various examples such as combining the above-mentioned embodiments and the above-mentioned modifications are used as long as the object of the present invention is not deviated. Can be transformed.

10, 11, 12, 13, 14, 15, 16, 17, 18, 19, 20 ... Vehicle automatic transmission, B1 ... 1st brake, B2 ... 2nd brake, B3 ... 3rd brake, C1 ... 1st Carrier, C2 ... 2nd carrier, C3 ... 3rd carrier, C4 ... 4th carrier, CL1-... 1st clutch, CL2 ... 2nd clutch, CL3 ... 3rd clutch, CL4 ... 4th clutch, H ... Transmission case, J1 ... 1st connecting member, J2 ... 2nd connecting member, J3 ... 3rd connecting member, J4 ... 4th connecting member, J5 ... 5th connecting member, J6 ... 6th connecting member, J7 ... 7th connecting member, J8 ... Eighth connecting member, J9 ... Ninth connecting member, J10 ... Tenth connecting member, J11 ... Eleventh connecting member, J12 ... Twelfth connecting member, L ... Axis line, N ... Input shaft, P1 ... First planetary Mechanism, P2 ... 2nd planetary mechanism, P3 ... 3rd planetary mechanism, P4 ... 4th planetary mechanism, Q1 ... 1st pinion gear, Q2 ... 2nd pinion gear, Q3 ... 3rd pinion gear, Q4 ... 4th pinion gear, R1 ... 1 ring gear, R2 ... 2nd ring gear, R3 ... 3rd ring gear, R4 ... 4th ring gear, S1 ... 1st sun gear, S2 ... 2nd sun gear, S3 ... 3rd sun gear, S4 ... 4th sun gear, T ... output shaft

Claims (8)

Input axis and
Output axis and
A first planetary mechanism, a second planetary mechanism, a third planetary mechanism, and a fourth planetary mechanism, which are arranged between the input shaft and the output shaft and have a first element, a second element, and a third element, respectively.
The seven engaging elements of the first clutch, the second clutch, the third clutch, the fourth clutch, the first brake, the second brake and the third brake,
A first connecting member that brings the first element of the first planetary mechanism and the fixing member into a disengageable connection state,
A second connecting member that connects the second element of the first planetary mechanism and the third element of the second planetary mechanism in a connected state.
A third connecting member that connects the third element of the first planetary mechanism and the input shaft, and
A fourth connecting member that connects the first element of the second planetary mechanism and the first element of the third planetary mechanism in a connected state.
A fifth connecting member that connects the second element of the third planetary mechanism and the output shaft, and
A sixth connecting member that connects the third element of the third planetary mechanism and the fixing member, and a sixth connecting member.
The first element of the fourth planetary mechanism and the first element of the third planetary mechanism, or the first element of the fourth planetary mechanism and the third element of the third planetary mechanism are connected. The seventh connecting member to be in a state,
An eighth connecting member that connects the second element and the input shaft of the fourth planetary mechanism, or the third element and the input shaft of the fourth planetary mechanism, in a connected state.
A ninth connecting member for connecting the third element and the output shaft of the fourth planetary mechanism or the second element and the output shaft of the fourth planetary mechanism in a connected state is provided.
The first brake allows the first element of the first planetary mechanism to be engaged and disengaged from the fixing member.
The second brake allows the second element of the second planetary mechanism to be engaged and disengaged from the fixing member.
The third brake makes it possible to engage and disengage the third element of the third planetary mechanism with respect to the fixing member.
The first clutch engages the input shaft and the second element of the second planetary mechanism in a disengageable manner.
The second clutch detachably connects two elements of the first element, the second element and the third element of the second planetary mechanism.
The third clutch engages and disengages the third element of the fourth planetary mechanism with one of the eighth connecting member and the ninth connecting member.
The fourth clutch is two of the first element, the second element and the third element of the first planetary mechanism, the second planetary mechanism, the third planetary mechanism and the fourth planetary mechanism, respectively. The two elements are connected in a clutchable manner,
An automatic transmission for a vehicle configured to engage three of the seven engaging elements. The fourth clutch is
The automatic vehicle transmission according to claim 1, wherein two elements of the first element, the second element, and the third element of the first planetary mechanism are detachably connected to each other. The first planetary mechanism, the second planetary mechanism, the third planetary mechanism, and the fourth planetary mechanism are
Along the axis of the input shaft, the first planetary mechanism, the second planetary mechanism, the third planetary mechanism, and the fourth planetary mechanism are arranged in this order from the side of the input shaft toward the side of the output shaft. The vehicle automatic transmission according to claim 1 or 2. The third planetary mechanism and the fourth planetary mechanism are
The automatic transmission for a vehicle according to claim 1 or 2, which is arranged in a direction perpendicular to the axis of the input shaft. The first planetary mechanism, the second planetary mechanism, the third planetary mechanism, and the fourth planetary mechanism are single pinion type planetary mechanisms.
The first element of the first planetary mechanism, the third element of the second planetary mechanism, the first element of the third planetary mechanism, and the first element of the fourth planetary mechanism are sun gears.
The second element of the first planetary mechanism, the second element of the second planetary mechanism, the second element of the third planetary mechanism, and the second element of the fourth planetary mechanism are carriers.
The third element of the first planetary mechanism, the first element of the second planetary mechanism, the third element of the third planetary mechanism, and the third element of the fourth planetary mechanism are ring gears. The vehicle automatic transmission according to any one of 1 to 4. The first planetary mechanism is a double pinion type planetary mechanism.
The second planetary mechanism, the third planetary mechanism, and the fourth planetary mechanism are single pinion type planetary mechanisms.
The first element of the first planetary mechanism, the first element of the second planetary mechanism, the first element of the third planetary mechanism, and the first element of the fourth planetary mechanism are sun gears.
The third element of the first planetary mechanism, the second element of the second planetary mechanism, the second element of the third planetary mechanism, and the second element of the fourth planetary mechanism are carriers.
The second element of the first planetary mechanism, the third element of the second planetary mechanism, the third element of the third planetary mechanism, and the third element of the fourth planetary mechanism are ring gears, claim. The vehicle automatic transmission according to any one of items 1 to 4. The first planetary mechanism and the second planetary mechanism are double pinion type planetary mechanisms.
The third planetary mechanism and the fourth planetary mechanism are single pinion type planetary mechanisms.
The first element of the first planetary mechanism, the first element of the second planetary mechanism, the first element of the third planetary mechanism, and the first element of the fourth planetary mechanism are sun gears.
The third element of the first planetary mechanism, the third element of the second planetary mechanism, the second element of the third planetary mechanism, and the second element of the fourth planetary mechanism are carriers.
The second element of the first planetary mechanism, the second element of the second planetary mechanism, the third element of the third planetary mechanism, and the third element of the fourth planetary mechanism are ring gears, claim. The vehicle automatic transmission according to any one of items 1 to 4. The first planetary mechanism and the second planetary mechanism are double pinion type planetary mechanisms.
The third planetary mechanism and the fourth planetary mechanism are single pinion type planetary mechanisms.
The first element of the first planetary mechanism, the first element of the second planetary mechanism, the first element of the third planetary mechanism, and the first element of the fourth planetary mechanism are sun gears.
The third element of the first planetary mechanism, the third element of the second planetary mechanism, the second element of the third planetary mechanism, and the second element of the fourth planetary mechanism are carriers.
The second element of the first planetary mechanism, the second element of the second planetary mechanism, the third element of the third planetary mechanism, and the third element of the fourth planetary mechanism are ring gears.
The fourth clutch is
The automatic vehicle transmission according to claim 1, wherein the third element of the second planetary mechanism and the second element of the third planetary mechanism are detachably connected to each other.

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