JP2019002501A - Automatic gear change device for vehicle - Google Patents

Abstract

To provide an automatic gear change device for a vehicle which can obtain a multi-gear change stage by suppressing the deterioration of a gear change shock and expanding a spread.SOLUTION: In an automatic gear change device 10 for a vehicle, a first brake B1 makes a first sun gear S1 of a first planetary mechanism P1 engaged with and disengaged from a transmission case H, a second brake B2 makes a second carrier C2 of a second planetary mechanism P2 engaged with and disengaged from the case H, a third brake B3 makes a third ring gear R3 of a third planetary mechanism P3 engaged with and disengaged from the case H, a first clutch CL1 connects an input shaft N and the second carrier C2 so as to be engaged with and disengaged from each other, a second clutch CL2 connects a second sun gear S2 and the second carrier C2 so as to be engaged with and disengaged from each other, a third clutch CL3 connects a fourth ring gear R4 of a fourth planetary mechanism P4 and a ninth connecting member J9 so as to be engaged with and disengaged from each other, and a fourth clutch CL4 connects a first carrier C1 and a first ring gear R1 so as to be engaged with and disengaged from each other.SELECTED DRAWING: Figure 2

Description

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

  Conventionally, for example, an automatic transmission for a vehicle disclosed in Patent Document 1 below is known. This conventional automatic transmission for a vehicle includes four planetary mechanisms having a first element, a second element, and a third element, a first engagement element, a second engagement element, a first clutch, a second clutch, It has six engaging elements: three clutches and first brake. And in the conventional automatic transmission for vehicles, the forward ninth speed and the reverse first speed are formed by engaging three engaging elements of the six engaging elements.

JP 2017-32026 A

  In recent years, in order to improve the fuel efficiency of a vehicle, like the conventional automatic transmission for a vehicle described above, it has been actively proposed to make the automatic transmission for a vehicle have multiple shift stages. In such a multi-shift stage, the gear ratio of each shift stage is set so that an efficient rotation speed range can be used when an engine or the like as a drive source generates drive force. However, when the spread in the automatic transmission for a vehicle is increased for the purpose of further increasing the number of shift stages, it is generally necessary to change the gear ratio of each shift stage with respect to the widened spread. For this reason, there is a case where the step ratio between the gear ratios is increased, and there is a possibility that the shift shock is worsened by increasing the step ratio. Further, with the change in gear ratio, there is a possibility that an efficient rotation speed range when 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 that can suppress the deterioration of a shift shock and widen a spread to make a multi-shift stage.

  In order to solve the above-described problem, an automatic transmission for a vehicle according to claim 1 is arranged between an input shaft, an output shaft, and an input shaft and an output shaft, and includes a first element and a second element. And a first planetary mechanism, a second planetary mechanism, a third planetary mechanism and a fourth planetary mechanism, and a first clutch, a second clutch, a third clutch, a fourth clutch, a first brake and a second, respectively. Seven engaging elements of the brake and the third brake, a first connecting member for detachably connecting the first element and the fixing member of the first planetary mechanism, the second element and the first planetary mechanism A second connecting member that connects the third element of the second planetary mechanism, a third connecting member that connects the third element of the first planetary mechanism and the input shaft, and a first element of the second planetary mechanism And the third planetary mechanism The fourth connecting member that connects the elements, the fifth connecting member that connects the second element of the third planetary mechanism and the output shaft, and the third element of the third planetary mechanism and the fixing member are connected. A sixth connecting member to be brought into a state, a first element of the fourth planetary mechanism and a first element of the third planetary mechanism, or a first element of the fourth planetary mechanism and a third element of the third planetary mechanism, A seventh connection member to be connected, a second element of the fourth planetary mechanism and the input shaft, or an eighth connection member to connect the third element of the fourth planetary mechanism and the input shaft; A third element of the four planetary mechanism and an output shaft, or a ninth connection member that connects the second element of the fourth planetary mechanism and the output shaft, and the first brake is the first planetary mechanism. The first element can be engaged and disengaged with respect to the fixing member. The brake allows the second element of the second planetary mechanism to be engaged and disengaged with respect to the fixed member, the third brake allows the third element of the third planetary mechanism to be engaged and disengaged with respect to the fixed member, and the first clutch The input shaft and the second element of the second planetary mechanism are detachably connected, and the second clutch engages two elements of the first element, the second element, and the third element of the second planetary mechanism. The third clutch is detachably connected to the third element of the fourth planetary mechanism and one of the eighth connection member and the ninth connection member. The fourth clutch is Two of the first, second, and third elements of the one planetary mechanism, the second planetary mechanism, the third planetary mechanism, and the fourth planetary mechanism are detachably connected, and the seven engagements Engage three of the elements, such as Configured.

  According to this, it is possible to widen the spread without changing the gear ratio forming each shift stage in the vehicle automatic transmission. As a result, the step ratio of the vehicle automatic transmission does not increase, and the shift shock at the time of shifting does not worsen. Therefore, an extremely smooth shift can be realized in the vehicle automatic transmission. Further, in the automatic transmission for a vehicle, 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. be able to. Thereby, the fuel consumption of the vehicle is not deteriorated.

It is a skeleton figure showing typically the automatic transmission for vehicles in a first embodiment. It is a figure which shows the operating state of the clutch and brake in each gear stage of the automatic transmission for vehicles of FIG. FIG. 2 is a velocity diagram of the vehicle automatic transmission device of FIG. 1. 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 vehicles in a second embodiment. It is a figure which shows the operating state of the clutch and brake in each gear stage of the automatic transmission for vehicles of FIG. FIG. 14 is a velocity diagram of the vehicle automatic transmission device of FIG. 13.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to the drawings. In the following embodiments and modifications, portions that are the same or equivalent to each other are denoted by the same reference numerals in the drawings. Each figure used for explanation is a conceptual diagram, and the shape of each part may not necessarily be exact.

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

  In addition, the apparatus 10 includes four single-pinion type first planetary mechanisms P1, second planetary mechanisms P2, and a second planetary mechanism P2, which are arranged in order along the axis L of the input shaft N between the input shaft N and the output shaft T. A third planetary mechanism P3 and a 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 in parallel from the input shaft N to the output shaft T in this order. Further, the device 10 includes seven engagement elements including a first clutch CL1, a second clutch CL2, a third clutch CL3, a fourth clutch CL4, and a first brake B1, a second brake B2, and a third brake B3. I have.

  The first planetary mechanism P1 includes a first sun gear S1 as a first element that is rotatably supported coaxially with an axis L, a first ring gear R1 as a third element, and a first sun gear S1 and a first ring gear R1. The first carrier C1 as a second element that rotatably supports the first pinion gear Q1 meshing with the first pinion gear Q1. 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. The second carrier C2 as a second element that rotatably supports the second pinion gear Q2 meshing with the second pinion gear Q2. 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. Is constituted by a third carrier C3 as a second element that rotatably supports a third pinion gear Q3 meshing with the gear. 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. And a fourth carrier C4 as a second element that rotatably supports the fourth pinion gear Q4.

  The first clutch CL1 to the fourth clutch CL4 are engaging elements that can selectively engage and disengage a plurality of elements. The first clutch CL <b> 1 to the fourth clutch CL <b> 4 are normally open types and are hydraulic types that are operated by supplied hydraulic pressure. As a result, the first clutch CL1 to the fourth clutch CL4 receive hydraulic pressure from the hydraulic pump that operates based on the control command from the transmission ECU (TM-ECU) via the oil passage formed in the input shaft N and the transmission case H. When supplied, a plurality of clutch plates (not shown) are brought into contact, and the elements are engaged with each other so that the driving force is transmitted between the target elements. Then, by separating the clutch plates, 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 detachable manner. The second clutch CL2 integrally rotates the second planetary mechanism P2, and can disengage and disengage two elements of the second sun gear S2, the second ring gear R2, and the second carrier C2 of the second planetary mechanism P2. To do. Specifically, in the present embodiment, as shown in FIG. 1, the second clutch CL <b> 2 connects the second sun gear S <b> 2 and the second carrier C <b> 2 so that they can be engaged and disengaged. The third clutch CL3 is detachably connected to one of an eighth connecting member J8 and a ninth connecting member J9, which will be described later. As shown in FIG. 1, the third carrier C3 of the third planetary mechanism P3 and The output shaft T and the fourth ring gear R4 of the fourth planetary mechanism P4 are detachably connected. The fourth clutch CL4 integrally rotates the first planetary mechanism P1, and can engage 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 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 detachable manner.

  The first brake B1 to the third brake B3 are engagement elements that are provided in the transmission case H and brake the rotation of predetermined elements. The first brake B1 to the third brake B3 are of a hydraulic type that is operated by the supplied hydraulic pressure. Accordingly, when the first brake B1 to the third brake B3 are supplied with hydraulic pressure via an oil passage formed in the transmission case H from a hydraulic pump that operates based on a control command from the TM-ECU, a disk (not shown) The pad is pressed to brake the rotation of a predetermined target element. Then, the predetermined element is allowed to rotate by separating the pad from the disk.

  The first brake B1 allows the first sun gear S1 of the first planetary mechanism P1 to be engaged with and disengaged from the transmission case H, as shown in FIG. The second brake B2 enables the second carrier C2 of the second planetary mechanism P2 to be engaged with and disengaged from the transmission case H, as shown in FIG. The third brake B3 allows the third ring gear R3 of the third planetary mechanism P3 to be engaged with and disengaged from the transmission case H as shown in FIG.

  Further, in the apparatus 10, as shown in FIG. 1, the elements 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 one of the first connecting member J1 to the twelfth connecting member J12. 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 one of the first connecting member J1 to the eleventh connecting member J11. The 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 one of the first connecting member J1 to the eleventh connecting member J11. The

  Specifically, as shown in FIG. 1, the first connecting member J <b> 1 brings the first sun gear S <b> 1 of the first planetary mechanism P <b> 1 into a connected state that can be engaged and disengaged with the first brake B <b> 1 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 and the input shaft N of the first planetary mechanism P1.

  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 J <b> 6 brings the third ring gear R <b> 3 of the third planetary mechanism P <b> 3 into a connected state that can be engaged with and disengaged from the third brake B <b> 3 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 and the input shaft N of the fourth planetary mechanism P4.

  As shown in FIG. 1, the ninth connection member J9 is a connection that allows the fourth ring gear R4 of the fourth planetary mechanism P4 to be engaged with and disengaged from the output shaft T via the third clutch CL3 provided on the fifth connection 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 the second carrier B2 provided in the transmission case H can be engaged and disengaged. The twelfth connecting member J12 connects the fifth connecting member J5 and the output shaft T.

  The device 10 of the present embodiment configured as described above is engaged with three engagement elements of the first clutch CL to the fourth clutch CL4 and the first brake B1 to the third brake B3. This is an automatic transmission capable of forming two forward speeds of 10 forward and reverse speeds having reverse (High and Low), 1st speed to 6th speed underdrive, and 7th speed 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 to reverse by reverse (Low). 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 ), The vehicle is caused to travel in reverse by reverse (High), which has a larger rotational speed.

  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 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, the first clutch CL1 and the third clutch CL3 are only engaged and the third speed is engaged. When only the three brake B3 is engaged, the fourth speed is achieved. 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. If it is done, it will become 6 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 CL When only the three clutch CL3 is engaged and only the second brake B2 is engaged, the eighth speed is set. When only the third clutch CL3 is engaged and only the first brake B1 and the second brake B2 are engaged, the third clutch CL3 and the fourth clutch CL4 are engaged and the ninth speed is engaged. When only the two brakes B2 are engaged, the tenth speed is achieved.

  By the way, in the device 10, the ratio of the low-side gear ratio to the high-side gear ratio (= (low-side gear ratio) / () without changing the gear ratios in the above-described conventional automatic transmission for vehicles. The spread representing the high gear ratio)) is widened, and the forward 10 speed can be achieved. Hereinafter, this will be specifically described based on the velocity diagrams shown in FIGS. 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 at each shift speed, and the elements of the first planetary mechanism P1 to the fourth planetary mechanism P4 are shown. They are arranged at intervals (1: λ) corresponding to the gear ratio (λ) in the horizontal axis direction and the vertical axis direction, and the speed ratio of each element is taken in the vertical axis direction. Moreover, the speed line shown by the thick solid line in FIG. 3 shows the speed line when the fourth clutch CL4 is engaged.

  When the device 10 (same as the above-described conventional automatic transmission for vehicles) forms the ninth speed, the first ring gear R1 of the first planetary mechanism P1 is connected by the third connecting member J3 as shown in FIG. Rotation is input from the input shaft N (see FIG. 1), and the first sun gear S1 is fixed by the first brake B1. Thereby, in the 1st planetary mechanism P1, the rotation speed of the 1st carrier C1 is made. 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 planetary mechanism P2 is connected to the second planetary mechanism P2. The carrier C2 is fixed by the second brake B2 via the eleventh connecting member J11. Thereby, in the 2nd planetary mechanism P2, the reverse rotation speed of 2nd ring gear R2 is made.

  Further, the fourth carrier C4 of the fourth planetary mechanism P4 receives rotation input from the input shaft N connected by the eighth connecting member J8 (see FIG. 1), and the fourth sun gear S4 of the fourth planetary mechanism P4 and the fourth sun gear S4. The second ring gear R2 of the two planetary mechanism P2 is connected by a fourth connecting member J4 and a seventh connecting member J7 (see FIG. 1). Thereby, in the 4th planetary mechanism P4, the rotation speed of 4th ring gear R4 is made. 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 a fourth connecting member J4 (see FIG. 1), and the third carrier C3 of the third planetary mechanism P3 and the second carrier C3. 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. Thereby, the rotation speed of the 3rd carrier C3 of the 3rd planetary mechanism P3 is made. When the ninth speed is established, the third ring gear R3 of the third planetary mechanism P3 is not fixed by the third brake B3 and thus freely rotates. 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 rotational speed of the third carrier C3 is transmitted to the output shaft T. Is 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 sun gear S1 as compared with the case where the ninth speed described above 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 are connected to the fourth through the tenth connecting member J10, compared with the case where the ninth speed is formed. The difference is 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 rotational speed of the second sun gear S2 of the second planetary mechanism P2 increases and the reverse rotational speed of the second ring gear R2 of the second planetary mechanism P2 also increases as compared to the ninth speed. 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 increase, and the increased rotation of the third carrier C3. The number is transmitted to the output shaft T. Thereby, as shown in FIG. 3, the spread in the apparatus 10 spreads.

  Also, when the device 10 forms 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 are connected via the tenth connecting member J10. The fourth clutch CL4 is connected to rotate integrally. Therefore, when the increased rotation speed of the third carrier C3 is transmitted to the output shaft T, it is possible to form reverse (High) in the apparatus 10.

  As can be understood from the above description, the vehicular automatic transmission 10 according to the above-described embodiment is disposed between the input shaft N, the output shaft T, and the input shaft N and the output shaft T, so that the first element A first sun gear S1, a second ring gear R2, a third sun gear S3 and a fourth sun gear S4, a first carrier C1, a second carrier C2, a third carrier C3 and a fourth carrier C4 as second elements, A first planetary mechanism P1, a second planetary mechanism P2, a third planetary mechanism P3, and a fourth planetary mechanism P4 each 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; , First clutch CL1, second clutch CL2, third clutch CL3, fourth clutch CL4, first brake B1, second brake B2, and third brake B Of the first planetary mechanism P1, the first sun gear S1 of the first planetary mechanism P1 and the transmission case H as a fixing member are connected in a detachable connection state, and the first planetary mechanism P1 A third connection member J2 for connecting one carrier C1 and the second sun gear S2 of the second planetary mechanism P2 and a third connection member for connecting the first ring gear R1 and the input shaft N of the first planetary mechanism P1. The member J3, the fourth connecting member J4 for connecting the second ring gear R2 of the second planetary mechanism P2 and the third sun gear S3 of the third planetary mechanism P3, the third carrier C3 and the output of the third planetary mechanism P3 A fifth connecting member J5 that connects the shaft T to the connected state, a sixth ring gear R3 of the third planetary mechanism P3, and a transmission case H that connects the shaft T to the sixth state. The connecting member J6, the seventh connecting member J7 for connecting the fourth sun gear S4 of the fourth planetary mechanism P4 and the third sun gear S3 of the third planetary mechanism P3, and the fourth carrier C4 of the fourth planetary mechanism P4 An eighth connecting member J8 for connecting the input shaft N, and a ninth connecting member J9 for connecting the fourth ring gear R4 of the fourth planetary mechanism P4 and the output shaft T, and the first brake B1 Can engage / disengage the first sun gear S1 of the first planetary mechanism P1 with respect to the transmission case H, and the second brake B2 can engage / disengage the second carrier C2 of the second planetary mechanism P2 with respect to the transmission case H. The third brake B3 allows the third ring gear R3 of the third planetary mechanism P3 to be engaged with and disengaged from the transmission case H, and the first clutch C L1 releasably connects the input shaft N and the second carrier C2 of the second planetary mechanism P2, and the second clutch CL2 includes 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 which is two elements of the ring gear R2 and the second carrier C2 are detachably connected, and the third clutch CL3 is connected to the fourth ring gear R4 of the fourth planetary mechanism P4 and the eighth connecting member. J8 and the ninth connecting member J9, which is one of the ninth connecting members J9, are detachably connected, and the fourth clutch CL4 includes 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 of the P3 and the fourth planetary mechanism P4, the first carrier C1, the second carrier C2, the second The first carrier C1 and the first carrier C1 of the first planetary mechanism P1, which are two elements of the carrier C3 and the fourth carrier C4, and the first ring gear R1, the second ring gear R2, the third ring gear R3, and the fourth ring gear R4. The ring gear R1 is detachably connected, and is configured to engage three of the seven engagement 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 arranged on the output shaft T from the input shaft N side 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, it is possible to widen the spread without changing the gear ratios forming the respective shift stages in the vehicle automatic transmission 10. As a result, the step ratio of the vehicle automatic transmission 10 is not increased, and the shift shock at the time of shifting is not deteriorated. Therefore, in the vehicular automatic transmission 10, an extremely smooth shift can be realized. Further, in the vehicle automatic transmission 10, it is not necessary to change the gear ratio in order to widen the spread, so when the engine that is the driving source generates the driving force, the efficient engine speed range is used. can do. Thereby, the fuel consumption of the vehicle is not deteriorated.

  Further, the first planetary mechanism in which 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 and the first ring gear R1 among the first sun gear S1, the first carrier C1, and the first ring gear R1 of the mechanism P1, the first planetary mechanism P1 can be rotated integrally. Thereby, the spread of the vehicle automatic transmission 10 can be appropriately widened without being excessively widened, and an increase in the step ratio due to the multiple shift speeds 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 by only a single pinion type planetary mechanism. Thereby, the structure of the 1st planetary mechanism P1, the 2nd planetary mechanism P2, the 3rd planetary mechanism P3, and the 4th 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 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. In the second planetary mechanism P2, the second sun gear S2 is a first element, the second carrier C2 is a second element, and the second ring gear R2 is a third element. 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 according to the first modification, the first carrier C1 of the first planetary mechanism P1 is changed to be connected by the second ring gear R2 of the second planetary mechanism P2 and the second connecting member J2. Therefore, the configuration differs from that of the apparatus 10. Further, in the automatic transmission device 11 for a vehicle, the device 10 is changed 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 a different configuration.

  In the vehicular automatic transmission 11 having such a configuration, as shown in FIG. 2, the first clutch CL <b> 1 to the fourth clutch CL <b> 4 and the first brake B <b> 1 to third as in the apparatus 10 of the first embodiment. By selectively engaging three of the seven engaging elements of the brake B3 and restricting 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 shift stage of two speeds and two reverse speeds.

(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 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. In the second planetary mechanism P2, the second sun gear S2 is a first element, the second carrier C2 is a second element, and the second ring gear R2 is a third element. 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 by the second ring gear R2 of the second planetary mechanism P2 and the second connecting member J2. Therefore, the configuration differs from that of the apparatus 10. Further, in the automatic transmission device 12 for a vehicle, the device 10 is changed 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 a different configuration. In the vehicle automatic transmission 12, the fourth ring gear R 4 of the fourth planetary mechanism P 4 is connected to the fifth connecting member J 5 and the twelfth connecting member J 12, that is, the output shaft T by the ninth connecting member J 9. The configuration is different from that of the apparatus 10 in that it is changed.

  Furthermore, in the automatic transmission device 12 for a vehicle, the second clutch CL2 is changed so as to detachably connect the second carrier C2 of the second planetary mechanism P2 and the second ring gear R2 of the second planetary mechanism P2. Thus, the configuration is different from that of the apparatus 10. Further, in the vehicle automatic transmission device 12, the third clutch CL3 is changed so as to detachably connect the fourth carrier C4 of the fourth planetary mechanism P4 and the input shaft N via the eighth connecting member J8. Therefore, the configuration differs from that of the apparatus 10.

  In the vehicular automatic transmission 12 having such a configuration, as shown in FIG. 2, the first clutch CL <b> 1 to the fourth clutch CL <b> 4 and the first brake B <b> 1 to third as in the apparatus 10 of the first embodiment. By selectively engaging three of the seven engaging elements of the brake B3 and restricting 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 shift stage of two speeds and two reverse speeds.

(Third modification of the first embodiment)
Next, the configuration of a third modification of the first embodiment will be described with reference to FIG. 6 shown corresponding to FIG. The automatic transmission 13 for a vehicle according to the third modified example is different from the apparatus 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. In the second planetary mechanism P2, the second sun gear S2 is a first element, the second carrier C2 is a second element, and the second ring gear R2 is a third element. 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.

  Accordingly, in the automatic transmission 13 for a vehicle, the device 10 is changed in 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. Further, the vehicle automatic transmission 13 is different from the apparatus 10 in that the first carrier C1 of the first planetary mechanism P1 is changed to be connected by the input shaft N and the third connecting member J3. . In the automatic transmission 13 for a vehicle, the device 10 is changed 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 a different configuration.

  Further, in the vehicle automatic transmission device 13, the first clutch CL1 is changed so as to detachably connect the first carrier C1 of the first planetary mechanism P1 and the second carrier C2 of the second planetary mechanism P2. Thus, the configuration is different from that of the apparatus 10. In the automatic transmission 13 for a vehicle, the second clutch CL2 is changed so as to detachably connect the second sun gear S2 of the second planetary mechanism P2 and the second ring gear R2 of the second planetary mechanism P2. Thus, the configuration is different from that of the apparatus 10. Further, in the vehicle automatic transmission device 13, the third clutch CL3 is connected to the second sun gear S2 of the second planetary mechanism P2 and the fourth planetary mechanism P4 via the fourth connecting member J4 and the seventh connecting member J7. The configuration is different from that of the apparatus 10 in that the sun gear S4 is removably connected to the sun gear S4.

  Also in the automatic transmission 13 for a vehicle having such a configuration, as shown in FIG. 2, the first clutch CL <b> 1 to the fourth clutch CL <b> 4 and the first brake B <b> 1 to third as in the device 10 of the first embodiment. By selectively engaging three of the seven engaging elements of the brake B3 and restricting 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 shift stage of two speeds and two reverse speeds.

(Fourth modification of the first embodiment)
Next, the configuration of the fourth modification of the first embodiment will be described with reference to FIG. 7 shown corresponding to FIG. The automatic transmission 14 for a vehicle according to the fourth modified example is different from the apparatus 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. 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. 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 automatic transmission 14 for vehicles, the apparatus 10 is changed in 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. Further, in the vehicle automatic transmission device 14, the second sun gear S2 of the second planetary mechanism P2 is changed to be connected to the third sun gear S3 of the third planetary mechanism P3 by the fourth connecting member J4. It has a different configuration.

  Further, in the vehicle automatic transmission device 14, 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 planetary mechanism P2 is connected to the second shaft P2. The configuration differs from that of the apparatus 10 in that the ring gear R2 is connected so as to be detachable. Further, the vehicle automatic transmission 14 differs 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 has a configuration.

  In the vehicular automatic transmission 14 having such a configuration, as shown in FIG. 2, the first clutch CL <b> 1 to the fourth clutch CL <b> 4 and the first brake B <b> 1 to third as in the apparatus 10 of the first embodiment. By selectively engaging three of the seven engaging elements of the brake B3 and restricting 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 shift stage of two speeds and two reverse speeds.

(Fifth modification of the first embodiment)
Next, the configuration of a fifth modification of the first embodiment will be described with reference to FIG. 8 shown corresponding to 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. In the second planetary mechanism P2, the second sun gear S2 is a first element, the second carrier C2 is a second element, and the second ring gear R2 is a third element. 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 modified example, the third carrier C3 of the third planetary mechanism P3 is the fourth carrier C4 of the fourth planetary mechanism P4. And the fifth connecting member J5 is different from the apparatus 10 in that it is changed to be connected by the fifth connecting member J5. The device 15 is different from the device 10 in that the third ring gear R3 of the third planetary mechanism P3 is changed to be connected to the fourth sun gear S4 of the fourth planetary mechanism P4 by the seventh connecting member J7. It has become. The device 15 is different from the device 10 in that the first carrier C1 of the first planetary mechanism P1 is changed to be connected by the second ring gear R2 of the second planetary mechanism P2 and the second connecting member J2. It has become. The device 15 is different from the device 10 in that the second sun gear S2 of the second planetary mechanism P2 is changed to be 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 in that the third clutch CL3 is detachably connected to the fourth ring gear R4 of the fourth planetary mechanism P4 and the input shaft N via the eighth connecting member J8. It has a different configuration.

  Also in the apparatus 15 having such a configuration, as in the apparatus 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 engagement elements of the three engagement elements and restricting the rotation of each element of the first planetary mechanism P1 to the fourth planetary mechanism P4, the forward tenth speed stage, the reverse second speed A fast gear can be formed.

(Sixth modification of the first embodiment)
Next, the configuration of the sixth modification of the first embodiment will be described with reference to FIG. 9 shown corresponding to FIG. The automatic transmission 16 for a vehicle according to the sixth modified example is different from 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 device 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 differs from that of the device 15 in that it is changed to be a right angle. In the vehicle automatic transmission 16, the fourth sun gear S4 of the single pinion type fourth planetary mechanism P4 is integrally disposed on the outer peripheral side of the third ring gear R3 of the single pinion type third planetary mechanism P3. Thus, the configuration is different from that of the device 15 in that the seventh connecting member J7 is changed. Further, in the vehicle automatic transmission device 16, 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 planetary mechanism P3. The device 15 is different from the device 15 in that it is changed to be connected to the fifth connecting member J5 via the three carriers C3.

  Further, in the vehicle automatic transmission device 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. It differs from the apparatus 15 by the point which changed so that it might connect with.

  In the vehicular automatic transmission 16 having such a configuration, as shown in FIG. 2, as in the device 10 of the first embodiment (the device 15 of the fifth modification), the first clutch CL1 to the fourth clutch CL4, And, by selectively engaging three engagement elements of the seven engagement 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 limiting the above, it is possible to form a shift speed of 10 forward speeds and 2nd reverse speeds. 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 modification of the first embodiment)
Next, the structure of the seventh modification of the first embodiment will be described with reference to FIG. 10 shown corresponding to 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. In the second planetary mechanism P2, the second ring gear R2 is a first element, the second carrier C2 is a second element, and the second sun gear S2 is a third element. 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 according to the seventh modification, the second sun gear S2 of the second planetary mechanism P2 is changed to be connected by the first carrier C1 of the first planetary mechanism P1 and the second connecting member J2. Therefore, the configuration is different from that of the device 15. Further, in the vehicle automatic transmission device 17, the device 15 is changed in 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.

  Also in the vehicle automatic transmission 17 having such a configuration, as shown in FIG. 2, as in the device 10 of the first embodiment (the device 15 of the fifth modification), the first clutch CL1 to the fourth clutch CL4, And, by selectively engaging three engagement elements of the seven engagement 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 limiting the above, it is possible to form a shift speed of 10 forward speeds and 2nd reverse speeds.

  In the fifth, sixth, and seventh modifications of the first embodiment, the vehicle automatic transmissions 15, 16, and 17 also have, as shown in FIGS. 6 and 7, for example, It is possible to change the one planetary mechanism P1 to a double pinion type, or to change the second planetary mechanism P2 to a double pinion type.

(Eighth modification of the first embodiment)
Next, the configuration of the eighth modification of the first embodiment will be described with reference to FIG. 11 showing a part corresponding to FIG. In the vehicle automatic transmission 18 according to 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. Thus, the configuration differs from that of the apparatus 10.

  Also 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, so that the first The first sun gear S1, the first ring gear R1, and the first carrier C1 of the planetary mechanism P1 can be rotated together. Accordingly, in the vehicle automatic transmission 18 as well, 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 engagement elements among the seven engagement elements and restricting the rotation of each element of the first planetary mechanism P1 to the fourth planetary mechanism P4, the forward tenth speed stage, the reverse movement A second gear can be formed.

(Ninth Modification of First Embodiment)
Next, the configuration of the ninth modification of the first embodiment will be described with reference to FIG. 12 showing a part corresponding to FIG. In the vehicle automatic transmission 19 of the ninth modified example, 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. Thus, the configuration differs from that of the apparatus 10.

  Also 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, so that the first The first sun gear S1, the first ring gear R1, and the first carrier C1 of the planetary mechanism P1 can be rotated together. Therefore, also in the automatic transmission 19 for vehicles, 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 engagement elements among the seven engagement elements and restricting the rotation of each element of the first planetary mechanism P1 to the fourth planetary mechanism P4, the forward tenth speed stage, the reverse movement A second gear can be formed.

(Second embodiment)
Next, a second embodiment of the present invention will be described. The automatic transmission 20 for a vehicle according to the second embodiment (hereinafter also simply referred to as “device 20”) has the first planetary mechanism P1 and the second planetary mechanism P2 changed to a double pinion type as shown in FIG. In this regard, the configuration is different from the apparatus 10 of the first embodiment shown in FIG. 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. The configuration is different from that of the apparatus 10 in that it is changed. 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 apparatus 10 in that it is changed.

  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 second planetary mechanism P2 The structure is different from that of the apparatus 10 in that the two ring gear R2 (second element) is removably connected. Also in the device 20, the second clutch CL2 couples the second sun gear S2 of the second planetary mechanism P2 and the second carrier C2 of the second planetary mechanism P2 in a detachable 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 has a configuration.

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

  The device 20 of the second embodiment configured as described above is configured by engaging three engagement elements of the first clutch CL to the fourth clutch CL4 and the first brake B1 to the third brake B3. This is an automatic transmission capable of forming a forward 12-speed reverse gear having reverse, first-speed to eighth-speed underdrive, and ninth-speed to twelve-speed overdrive. 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 The vehicle is driven in reverse by reverse rotation.

  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 CL 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, the first clutch CL1 and the fourth clutch CL4 are engaged in the third speed and the first clutch CL1 is engaged. When only the three brake B3 is 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, the third clutch CL3 and only the fourth clutch CL4 are engaged and the fifth clutch is engaged. When only one brake B1 is engaged, the sixth speed is set. 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 is supposed to 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 CL When only the three clutch CL3 is engaged and only the second brake B2 is engaged, the tenth speed is achieved. In addition, when only the third clutch CL3 is engaged and only the first brake B1 and the second brake B2 are engaged, the third clutch CL3 and the fourth clutch CL4 are only engaged. When only the second brake B2 is engaged, the twelfth speed is achieved.

  By the way, also in the device 20 in the second embodiment, the ratio of the low-side gear ratio to the high-side gear ratio (= (Low-side) without changing each gear ratio in the above-described conventional automatic transmission for vehicles. ) / (High side gear ratio)) can be widened to achieve a forward twelfth speed. Hereinafter, this will be specifically described based on the velocity diagrams shown in FIGS. 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 at each shift speed, and the elements of the first planetary mechanism P1 to the fourth planetary mechanism P4 are shown. They are arranged at intervals (1: λ) corresponding to the gear ratio (λ) in the horizontal axis direction and the vertical axis direction, and the speed ratio of each element is taken in the vertical axis direction. A speed line indicated by a thick solid line in FIG. 15 indicates a speed line when the fourth clutch CL4 is engaged.

  When the apparatus 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. The first sun gear S1 is fixed by the first brake B1. Thereby, in the 1st planetary mechanism P1, the rotation speed of 1st ring gear R1 is made. 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 planetary mechanism P2 The ring gear R2 is fixed by the second brake B2 via the eleventh connecting member J11. Thereby, in the 2nd planetary mechanism P2, the reverse rotation speed of 2nd sun gear S2 is made.

  The fourth carrier C4 of the fourth planetary mechanism P4 receives rotation input from the input shaft N connected by the eighth connecting member J8 (see FIG. 13), and the fourth sun gear S4 of the fourth planetary mechanism P4 and the fourth sun gear S4. The second sun gear S2 of the two planetary mechanism P2 is connected by a fourth connecting member J4 and a seventh connecting member J7 (see FIG. 13). Thereby, in the 4th planetary mechanism P4, the rotation speed of 4th ring gear R4 is made. 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 a fourth connecting member J4 (see FIG. 13), and the third carrier C3 of the third planetary mechanism P3 and the second carrier C3. 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 (see FIG. 13). Thereby, the rotation speed of the 3rd carrier C3 of the 3rd planetary mechanism P3 is made. When the eleventh speed is established, 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 rotational speed of the third carrier C3 is transmitted to the output shaft T. Is done.

  On the other hand, when the apparatus 20 forms the twelfth speed, 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 described above is formed. It differs in that it is not fixed by the first brake B1. Further, when the device 20 forms the 12th speed, the second carrier C2 (third element) of the second planetary mechanism P2 and the third carrier of the third planetary mechanism P3, compared to the case where the 11th speed is formed. It differs from C3 (second element) in that it is connected by a fourth clutch CL4 via a tenth connecting member J10 and rotates integrally.

  When the twelfth speed is 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 planetary mechanism P3 of the third planetary mechanism P3 connected to the fourth ring gear R4 of the fourth planetary mechanism P4 by the third clutch CL3 via the fifth connecting member J5, and the second planetary mechanism. The second carrier C2 of P2 is connected via the tenth connecting member J10 by the fourth clutch CL4 (see FIG. 13). 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). Thereby, in the apparatus 20, when forming the 12th speed, 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. The number of revolutions is made.

  Thereby, 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 is created by the third clutch CL3. And since the 3rd carrier C3 is connected with the output shaft T via the 5th connection member J5 and the 12th connection member J12, the rotation speed of the 3rd carrier C3 is transmitted to the output shaft T (FIG. 13). Here, in the apparatus 20, when the 12th gear is formed, the third carrier CL2 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. As a result, the second carrier C2 and the fourth ring gear R4 rotate at the same speed. Therefore, in the case of forming the twelfth speed, the rotational speed of the fourth ring gear R4 of the fourth planetary mechanism P4 is larger than that at the time of the eleventh speed formation. Also grows. Thereby, as shown in FIG. 15, the spread in the apparatus 20 spreads.

  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, and the first element of the first planetary mechanism P1, the first element of the second planetary mechanism P2, the first element of the third planetary mechanism P3, and the fourth element. 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 third element, the second element of the third planetary mechanism P3, and the second element of the fourth planetary mechanism P4 are respectively the first carrier C1, the second Are the second element of the first planetary mechanism P1, the second element of the second planetary mechanism P2, the third element of the third planetary mechanism P3, and the fourth planetary mechanism P4. The third elements are a first ring gear R1, a second ring gear R2, a third ring gear R3, and a fourth ring gear R4, respectively, and the fourth clutch CL4 is a second carrier that is the third element of the second planetary mechanism P2. C2 and the third carrier C3 which is the second element of the third planetary mechanism P3 are detachably connected.

  According to this, it is possible to widen the spread 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 is not increased, and the shift shock at the time of shifting is not deteriorated. Therefore, in the vehicle automatic transmission device 20, an extremely smooth shift can be realized. Further, in the vehicle automatic transmission 20, there is no need to change the gear ratio in order to widen the spread, so when the engine that is the driving source generates driving force, an efficient engine speed range is used. can do. Thereby, the fuel consumption of the vehicle is not deteriorated.

  In carrying out the present invention, the present invention is not limited to the above-described embodiments and the respective modifications. For example, various combinations such as the above-described embodiments and the respective modifications are possible without departing from the object of the present invention. Can be modified.

10, 11, 12, 13, 14, 15, 16, 17, 18, 19, 20 ... automatic transmission for vehicles, B1 ... first brake, B2 ... second brake, B3 ... third brake, C1 ... first Carrier, C2 ... second carrier, C3 ... third carrier, C4 ... fourth carrier, CL1 -... first clutch, CL2 ... second clutch, CL3 ... third clutch, CL4 ... fourth 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 ... 8th connecting member, J9 ... 9th connecting member, J10 ... 10th connecting member, J11 ... 11th connecting member, J12 ... 12th connecting member, L ... axis, N ... input shaft, P1 ... first planetary Mechanism, P2 ... Second planetary mechanism , P3 ... third planetary mechanism, P4 ... fourth planetary mechanism, Q1 ... first pinion gear, Q2 ... second pinion gear, Q3 ... third pinion gear, Q4 ... fourth pinion gear, R1 ... first ring gear, R2 ... second ring gear , R3 ... third ring gear, R4 ... fourth ring gear, S1 ... first sun gear, S2 ... second sun gear, S3 ... third sun gear, S4 ... fourth sun gear, T ... output shaft

Claims (8)

An input shaft;
An output shaft;
A first planetary mechanism, a second planetary mechanism, a third planetary mechanism, and a fourth planetary mechanism, each of which is disposed between the input shaft and the output shaft and has a first element, a second element, and a third element;
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 for connecting the first element of the first planetary mechanism and the fixing member so as to be disengageable;
A second connecting member for connecting the second element of the first planetary mechanism and the third element of the second planetary mechanism;
A third connecting member for connecting the third element of the first planetary mechanism and the input shaft;
A fourth connecting member for connecting the first element of the second planetary mechanism and the first element of the third planetary mechanism;
A fifth connecting member for connecting the second element of the third planetary mechanism and the output shaft;
A sixth connecting member for connecting the third element of the third planetary mechanism 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 of the fourth planetary mechanism and the third element of the third planetary mechanism are connected. A seventh connecting member to be in a state;
An eighth connecting member for connecting 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;
A third connecting member for connecting the third element of the fourth planetary mechanism and the output shaft or the second element of the fourth planetary mechanism and the output shaft;
The first brake is capable of engaging and disengaging the first element of the first planetary mechanism with respect to the fixing member,
The second brake is capable of engaging and disengaging the second element of the second planetary mechanism with respect to the fixing member,
The third brake is capable of engaging and disengaging the third element of the third planetary mechanism with respect to the fixing member;
The first clutch releasably connects the input shaft and the second element of the second planetary mechanism;
The second clutch releasably connects two elements of the first element, the second element, and the third element of the second planetary mechanism,
The third clutch releasably connects the third element of the fourth planetary mechanism and one of the eighth connection member and the ninth connection member,
The fourth clutch includes 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. Detachably connect two elements,
An automatic transmission for a vehicle configured to engage three of the seven engagement elements. The fourth clutch is
The automatic transmission for a vehicle according to claim 1, wherein two of the first element, the second element, and the third element of the first planetary mechanism are detachably connected. The first planetary mechanism, the second planetary mechanism, the third planetary mechanism, and the fourth planetary mechanism are:
The first planetary mechanism, the second planetary mechanism, the third planetary mechanism, and the fourth planetary mechanism are arranged in this order from the input shaft side to the output shaft side along the axis of the input shaft. The automatic transmission for a vehicle according to claim 1 or 2. The third planetary mechanism and the fourth planetary mechanism are:
The vehicular automatic transmission according to claim 1 or 2, wherein the automatic transmission is arranged in a direction perpendicular to an 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 automatic transmission for a vehicle according to any one of claims 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, The automatic transmission for a vehicle according to any one of claims 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 automatic transmission for a vehicle according to any one of claims 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 transmission for a vehicle 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.

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