JP2017172717A - Automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To shorten a shaft length more while a multi-stage formation of shift stage can be attained.SOLUTION: This invention is configured in such a way that a first carrier 21c of a first planetary gear 21 and a second carrier 22c of a second planetary gear 22 of an automatic transmission 20 are always connected through a first gear row G1 with a gear ratio gr1 and in turn, by a clutch C3, a first sun gear 21s of the first planetary gear 21 and a second sun gear 22s of a second planetary gear 22 can be connected to each other through a second gear row G2 with a gear ratio gr2, and, by a clutch C4, a first ring gear 21r of the first planetary gear 21 and a second ring gear 22r of the second planetary gear are connected to each other through a third gear row G3 with a gear ratio gr3.SELECTED DRAWING: Figure 1

Description

  The present invention disclosed herein relates to an automatic transmission.

  Conventionally, as this type of automatic transmission, one having four planetary gears, three clutches, and four brakes has been proposed (see, for example, FIG. 5 of Patent Document 1). In this automatic transmission, by selectively engaging two of the three clutches and the four brakes, the power input to the input shaft is changed to the forward speed from the first speed to the tenth speed. The speed can be changed to the reverse speed and output to the output shaft.

German Patent Application Publication No. 102013203607A1

  However, although the automatic transmission described above can form the forward speed from the first speed to the tenth speed, all four planetary gears, three clutches, and four brakes are coaxial with the input shaft. Therefore, there is a problem that the axial length becomes long.

  The main purpose of the automatic transmission according to the present disclosure is to further reduce the shaft length while enabling multi-stage shift stages.

  The invention of the present disclosure has taken the following means in order to achieve the main object described above.

The automatic transmission of the present disclosure is
An automatic transmission that shifts power input to an input shaft to a plurality of shift speeds and outputs the power to an output shaft arranged in parallel to the input shaft,
A first planetary gear having three rotating elements arranged coaxially with the input shaft;
A second planetary gear having three rotating elements arranged coaxially with the output shaft, the output shaft being always connected to any of the three rotating elements;
A first drive gear and a first driven gear meshing with each other, wherein the first drive gear is always connected to a predetermined one of the three rotating elements of the first planetary gear, and the second driven gear is A first gear train always connected to a predetermined one of the three rotating elements of the second planetary gear;
A second gear train including a second drive gear and a second driven gear meshing with each other, and having a gear ratio different from that of the first gear train;
A third gear train including a third drive gear and a third driven gear meshing with each other, and having a gear ratio different from that of the first gear train and the second gear train;
The second drive gear and the second driven gear are connected to another rotation element different from the one rotation element of the first planetary gear and another rotation element different from the one rotation element of the second planetary gear. A first engaging element that connects to each other and releases the connection between the two,
A remaining rotating element different from the one rotating element and the other rotating element of the first planetary gear and a remaining rotating element different from the one rotating element and the other rotating element of the second planetary gear; Are connected to each other via the third drive gear and the third driven gear, and a second engagement element for releasing the connection between them,
It is a summary to provide.

  According to the automatic transmission of the present disclosure, the first planetary gear, the second planetary gear in which the output shaft disposed in parallel with the input shaft is connected to any one of the three rotating elements, and the gear ratio are respectively set. The first, second, and third gear trains differing from each other, and the first and second engaging elements. The first gear train is always connected to a predetermined one of the three rotating elements of the first planetary gear and a predetermined one of the three rotating elements of the second planetary gear. The first engaging element is configured to connect the other rotating element of the first planetary gear and the other rotating element of the second planetary gear to each other via the second gear train and to release the connection between them. The second engaging element is configured to connect the remaining rotating elements of the first planetary gear and the remaining rotating elements of the second planetary gear to each other via the third gear train and to release the connection between them. . Thereby, the set of the first engagement element and the second gear train and the set of the second engagement element and the third gear train can be caused to function as a reduction gear or a speed-up gear with different gear ratios. Therefore, in the automatic transmission according to the present disclosure, two planetary gears can be omitted as compared with the configuration in which the reduction gear or the speed increasing gear is configured using the planetary gear and the engagement element (brake). In addition, since the first planetary gear is arranged coaxially with the input shaft, the second planetary gear is arranged coaxially with the output shaft arranged in parallel with the input shaft, so that two planetary gears are coaxial with the input shaft. The axial length can be shortened as compared with the case where the is disposed. As a result, the shaft length of the automatic transmission can be further shortened while making it possible to increase the number of shift stages.

1 is a schematic configuration diagram of a power transmission device including an automatic transmission according to an embodiment of the present disclosure. FIG. 2 is a velocity diagram showing a ratio of a rotational speed of each rotary element to an input rotational speed of the automatic transmission of FIG. 1. FIG. 2 is an operation table showing the relationship between each gear position of the automatic transmission of FIG. 1 and the operating states of clutches and brakes. It is a schematic block diagram of the power transmission device containing the automatic transmission of a modification. It is a schematic block diagram of the power transmission device containing the automatic transmission of a modification.

  Next, embodiments for carrying out the invention of the present disclosure will be described with reference to the drawings.

  FIG. 1 is a schematic configuration diagram of a power transmission device 10 including an automatic transmission 20 according to an embodiment of the present disclosure. As shown in FIG. 1, the power transmission device 10 is connected to a crankshaft of an engine (internal combustion engine) (not shown) and / or a rotor of an electric motor as a drive source mounted horizontally on the front portion of the front wheel drive vehicle. In addition, power (torque) from the engine or the like can be transmitted to left and right front wheels (drive wheels) (not shown). As shown in the figure, the power transmission device 10 includes a transmission case (stationary member) in addition to an automatic transmission 20 that shifts power transmitted from an engine or the like to an input shaft (input member) 20i and transmits it to the front wheels of the vehicle. 11 and fluid transmission device (starting device) 12 and the like.

  As shown in FIG. 1, the fluid transmission device 12 is configured as a fluid torque converter with a lock-up clutch including a pump impeller, a turbine runner, a stator, a one-way clutch, a lock-up clutch, and the like. The fluid transmission device 12 may be a simple fluid coupling.

  The automatic transmission 20 is configured as a 10-speed transmission, and as shown in FIG. 1, in addition to the input shaft 20i, a counter shaft extending in parallel with the input shaft (first shaft) 20i. (Second shaft) 40 includes an output shaft 20o arranged coaxially with the first planetary gear 21 of a double pinion type and a second planetary gear 22 of a single pinion type. In the present embodiment, the output shaft 20o is provided with an output gear of an external gear, a differential gear including a drive pinion gear meshing with the output gear, a differential ring gear meshing with the drive pinion gear (all not shown) ) To the left and right front wheels. Moreover, in this embodiment, the 1st planetary gear 21 is arrange | positioned coaxially with the input shaft 20i, and the 2nd planetary gear 22 is arrange | positioned coaxially with the output shaft 20o (counter shaft 40).

  The first planetary gear 21 of the double pinion type includes a first sun gear 21s (first rotating element) that is an external gear, and a first ring gear 21r (first gear) that is an internal gear arranged concentrically with the first sun gear 21s. A plurality of pairs of two pinion gears 21pa and 21pb that mesh with each other and one meshes with the first sun gear 21s and the other meshes with the first ring gear 21r. 1 carrier 21c (third rotating element).

  The first sun gear 21 s of the first planetary gear 21 is always connected to the input shaft 20 i and functions as an input element of the first planetary gear 21. A first drive gear 41, which is an external gear, is always connected coaxially to the first carrier 21c of the first planetary gear 21, and the first carrier 21c and the first drive gear 41 always rotate integrally. Or stop. The first drive gear 41 meshes with a first driven gear 42 that is an external gear, and constitutes a first gear train G1 together with the first driven gear 42. Further, a third drive gear 45, which is an external gear, is always connected coaxially to the first ring gear 21r of the first planetary gear 21, and the first ring gear 21r and the third drive gear 45 always rotate integrally. Or stop. The third drive gear 45 meshes with a third driven gear 46 that is an external gear, and constitutes a second gear train G3 together with the third driven gear 46. In the present embodiment, the first planetary gear 21 is configured such that the gear ratio λ1 (the number of teeth of the first sun gear 21s / the number of teeth of the first ring gear 21r) is, for example, λ1 = 0.250. .

  The single pinion type second planetary gear 22 includes a second sun gear 22s (fourth rotating element) that is an external gear, and a second ring gear 22r (second gear) that is an internal gear arranged concentrically with the second sun gear 22s. 6 rotation elements) and a second carrier 22c (fifth rotation element) holding a plurality of pinion gears 22p meshing with the second sun gear 22s and the second ring gear 22r so as to be rotatable (rotatable) and revolved.

  The second sun gear 22 s of the second planetary gear 22 is always connected to the counter shaft 40, and always rotates or stops integrally with the counter shaft 40. The counter shaft 40 is always connected coaxially with the second driven gear 44. The second driven gear 44 meshes with the second drive gear 43 that is an external gear, and the second drive gear 43 and the second driven gear 44 constitute a second gear train G2. The second carrier 22c of the second planetary gear 22 is always connected coaxially with the first driven gear 42, and always rotates or stops integrally with the first driven gear 42. Since the first drive gear 41 that constitutes the first gear train G1 together with the first driven gear 42 is always connected to the first carrier 22c of the first planetary gear 21, the second carrier 22c of the second planetary gear 22 is It is always connected to the first carrier 21c of the first planetary gear 21 via one gear train G1. The second ring gear 22r of the second planetary gear 22 is always connected to the output shaft 20o and functions as an output element of the second planetary gear 22. In the present embodiment, the second planetary gear 22 is configured such that the gear ratio λ2 (the number of teeth of the second sun gear 22s / the number of teeth of the second ring gear 22r) is, for example, λ2 = 0.500. .

  The first gear train G1, the second gear train G2, and the third gear train G3 are configured to have different gear ratios. In the present embodiment, the gear ratio gr1 (the number of teeth of the first driven gear 42 / the number of teeth of the first drive gear 41) of the first gear train G1 is set to gr1 = 1.000. The gear ratio gr2 of the second gear train G2 (the number of teeth of the second driven gear 44 / the number of teeth of the second drive gear 43) is determined to be larger than the gear ratio gr1 of the first gear train G1, and in this embodiment, , Gr2 = 1.550. The gear ratio gr3 of the third gear train G3 (the number of teeth of the third driven gear 46 / the number of teeth of the third drive gear 45) gr3 is larger than the gear ratio gr1 of the first gear train G1, and the second gear. It is determined to be smaller than the gear ratio gr2 of the row G2, and in this embodiment, gr3 = 1.250.

  Further, the automatic transmission 20 includes a clutch C1 (third engagement element), a clutch C2 (fourth engagement element), and a clutch C3 (first engagement element) for changing the power transmission path from the input shaft 20i to the output shaft 20o. Engagement element), clutch C4 (second engagement element), clutch C5 (seventh engagement element), brake B1 (fifth engagement element), and brake B2 (sixth engagement element).

  The clutch C1 connects the first sun gear 21s of the first planetary gear 21 and the first carrier 21c to each other and releases the connection between them. By connecting the first sun gear 21s of the first planetary gear 21 and the first carrier 21c, the three rotating elements of the first planetary gear 21 (first sun gear 21s, first ring gear 21r, and first carrier 21c) , Rotate or stop together.

  The clutch C2 connects the second sun gear 22s of the second planetary gear 22 and the second carrier 22c to each other and releases the connection between them. By connecting the second sun gear 22s of the second planetary gear 22 and the second carrier 22c, the three rotating elements (second sun gear 22s, second ring gear 22r, and second carrier 22c) of the second planetary gear 22 are connected. , Rotate or stop together.

  The clutch C3 connects and disconnects the first sun gear 21s of the first planetary gear 21 and the second drive gear 43 of the second gear train G2. Since the second drive gear 43 of the second gear train G2 is always connected to the second sun gear 22s of the second planetary gear 22 via the second driven gear 44 and the counter shaft 40, the first sun gear of the first planetary gear 21 is connected. The second sun gear 22s of the second planetary gear 22 is connected to the second planetary gear 22 via the second drive gear 43, the second driven gear 44, and the counter shaft 40 by being connected to the second drive gear 43 of the second gear train by the clutch C3. Will be connected to.

  The clutch C4 connects the third driven gear 46 of the third gear train G3 and the second ring gear 22r of the second planetary gear 22 to each other and releases the connection between them. Since the third driven gear 46 of the third gear train G3 is always connected to the first ring gear 21r of the first planetary gear 21 via the third drive gear 45, the third driven gear 46 of the third gear train G3 is connected by the clutch C4. Are connected to the second ring gear 22r of the second planetary gear 22, the first ring gear 21r of the first planetary gear 21 is connected to the second planetary gear 22 via the third drive gear 45 and the third driven gear 46. The second ring gear 22r (that is, the output shaft 20o) is connected.

  The clutch C5 connects and disconnects the first drive gear 41 of the first gear train G1 and the second drive gear 43 of the second gear train G2. The first drive gear 41 of the first gear train G1 is always connected to the second carrier 22c of the second planetary gear 22 via the first driven gear 42, and the second drive gear 43 of the second gear train G2 is connected to the second driven gear 44. Is always connected to the second sun gear 22s of the second planetary gear 22, via the clutch C5, the first drive gear 41 of the first gear train G1 and the second drive gear 43 of the second gear train G2 are connected. Thus, the second carrier 22c and the second sun gear 22s of the second planetary gear 22 are connected to each other via the first gear train G1 and the second gear train G2. Since the first drive gear 41 of the first gear train is always connected to the first carrier 21c of the first planetary gear 21, the first drive gear 41 and the second gear train of the first gear train G1 are connected by the clutch C5. When the second drive gear 43 of G2 is connected, the first carrier 21c of the first planetary gear 21 is connected to the second sun gear 22s of the second planetary gear 22 via the second gear train G2. become.

  The brake B1 fixes (connects) the first carrier 21c of the first planetary gear 21 to the transmission case 11 in a non-rotatable manner and releases the first carrier 21c from the transmission case 11. The first planetary gear 21c of the first planetary gear 21 is non-rotatably fixed to the transmission case 11 by the brake B1, so that the second planetary gear is always connected to the first carrier 21c via the first gear train G1. The second carrier 22c of 22 is also fixed to the transmission case 11 so as not to rotate.

  The brake B2 fixes (connects) the second drive gear 43 of the second gear train G2 to the transmission case 11 in a non-rotatable manner and releases the second drive gear 43 from being fixed to the transmission case 11. The second planetary gear 22 that is always connected to the second drive gear 43 via the second driven gear 44 when the second drive gear 43 of the second gear train G2 is fixed to the transmission case 11 in a non-rotatable manner by the brake B2. The second sun gear 22s is also fixed to the transmission case 11 so as not to rotate.

  In this embodiment, as the clutches C1, C2, C3, C4 and C5, a piston, a plurality of friction engagement plates (friction plates and separator plates), an engagement oil chamber to which hydraulic oil is supplied, a centrifugal hydraulic pressure cancellation chamber, and the like, respectively. A multi-plate friction type hydraulic clutch (friction engagement element) having a hydraulic servo constituted by is adopted. Also, as the brakes B1 and B2, a multi-plate friction hydraulic brake (having a hydraulic servo including a piston, a plurality of friction engagement plates (friction plates and separator plates), an engagement oil chamber to which hydraulic oil is supplied, etc.) A friction engagement element) is employed. The clutches C1 to C5 and the brakes B1 and B2 operate by receiving and supplying hydraulic oil from a hydraulic control device (not shown).

  FIG. 2 is a velocity diagram showing the ratio of the rotational speed of each rotary element to the rotational speed (input rotational speed) of the input shaft 20 i in the automatic transmission 20. (However, the rotational speed of the input shaft 20i, that is, the first sun gear 21s is a value of 1. The same applies hereinafter). Each speed diagram shown in FIG. 2 is, in order from the left end, the speed diagram of the first planetary gear 21, the speed diagram of the second planetary gear 22, the speed diagram of the first gear train G1, and the second gear. It is a speed diagram of row G2, and a speed diagram of third gear row G3. FIG. 3 is an operation table showing the relationship between the respective shift stages of the automatic transmission 20 and the operation states of the clutches C1 to C5 and the brakes B1 and B2.

  As shown in FIG. 2, the three rotating elements constituting the double pinion type first planetary gear 21, that is, the first sun gear 21 s, the first ring gear 21 r, and the first carrier 21 c, are speed lines of the first planetary gear 21. The first sun gear 21s, the first ring gear 21r, and the first carrier 21c are arranged in this order from the right side in the drawing at an interval corresponding to the gear ratio λ1 on the drawing (the leftmost velocity diagram in FIG. 2). According to the order of arrangement in the speed diagram, in the invention of the present disclosure, the first sun gear 21s is the first rotating element of the automatic transmission 20, the first ring gear 21r is the second rotating element of the automatic transmission 20, The first carrier 21 c is the third rotating element of the automatic transmission 20. Therefore, the first planetary gear 21 has the first rotation element, the second rotation element, and the third rotation element of the automatic transmission 20 that are arranged in order at intervals according to the gear ratio λ1 on the velocity diagram.

  As shown in FIG. 2, the three rotating elements constituting the single pinion type second planetary gear 22, that is, the second sun gear 22 s, the second ring gear 22 r, and the second carrier 22 c, are included in the second planetary gear 22. On the velocity diagram (second velocity diagram from the left end in FIG. 2), the second sun gear 22s, the second carrier 22c, and the second ring gear 22r are arranged in this order from the right side in the drawing at intervals corresponding to the gear ratio λ2. . According to the order of arrangement in the velocity diagram, in the invention of the present disclosure, the second sun gear 22s is the fourth rotating element of the automatic transmission 20, the second carrier 22c is the fifth rotating element of the automatic transmission 20, The second ring gear 22r is a sixth rotating element of the automatic transmission 20. Accordingly, the second planetary gear 22 has the fourth rotation element, the fifth rotation element, and the sixth rotation element of the automatic transmission 20 that are arranged in order at intervals according to the gear ratio λ2 on the velocity diagram.

  In the automatic transmission 20, the clutches C1 to C5 and the brakes B1 and B2 are engaged or released as shown in FIG. Between 20i and the output shaft 20o, 10 power transmission paths in the forward rotation direction and one in the reverse rotation direction, that is, the forward speed and the reverse speed from the first speed to the tenth speed can be formed. .

  Specifically, the forward first speed is formed by engaging the clutch C4 and the brake B1 and releasing the remaining clutches C1 to C3 and C5 and the brake B2. In forming the first forward speed, the clutch C4 causes the first ring gear 21r (second rotating element) of the first planetary gear 21 and the second ring gear 22r (sixth rotating element) of the second planetary gear 22 to be output shaft 22o. Are connected to each other via the third gear train G3. Further, the first carrier 21c (third rotating element) of the first planetary gear 21 and the second carrier 22c (fifth rotating element) of the second planetary gear 22 are fixed to the transmission case 11 so as not to rotate by the brake B1. The In this embodiment (when the gear ratios of the first and second planetary gears 21 and 22 are λ1 = 0.250 and λ2 = 0.500, the same applies hereinafter), the gear ratio at the first forward speed (input shaft 20i). Rotational speed / rotational speed of output shaft 20o) γ1 is γ1 = 5.000.

  The second forward speed is formed by engaging the clutch C4 and the brake B2 and releasing the remaining clutches C1 to C3 and C5 and the brake B1. In forming the second forward speed, the clutch C4 causes the first ring gear 21r (second rotating element) of the first planetary gear 21 and the second ring gear 22r (sixth rotating element) of the second planetary gear 22, that is, the output shaft 22o. Are connected to each other via the third gear train G3. Further, the second sun gear 22s (fourth rotating element) of the second planetary gear 22 is fixed to the transmission case 11 so as not to rotate by the brake B2. In the present embodiment, the gear ratio γ2 at the second forward speed is γ2 = 3.000. The step ratio between the first forward speed and the second forward speed is γ1 / γ2 = 1.667.

  The third forward speed is formed by engaging the clutches C4 and C5 and releasing the remaining clutches C1 to C3 and the brakes B1 and B2. In forming the third forward speed, the clutch C4 causes the first ring gear 21r (second rotating element) of the first planetary gear 21 and the second ring gear 22r (sixth rotating element) of the second planetary gear 22, that is, the output shaft 22o. Are connected to each other via the third gear train G3. Further, the second sun gear 22s (fourth rotating element) and the second carrier 22c (fifth rotating element) of the second planetary gear 22 are connected to each other via the first gear train G1 and the second gear train G2 by the clutch C5. At the same time, the first carrier 21c (third rotating element) of the first planetary gear 21 and the second sun gear 22s (fourth rotating element) of the second planetary gear 22 are connected to each other via the gear train G2. In the present embodiment, the gear ratio γ3 at the third forward speed is γ3 = 2.452. The step ratio between the second forward speed and the third forward speed is γ2 / γ3 = 1.223.

  The fourth forward speed is formed by engaging the clutches C2 and C4 and releasing the remaining clutches C1, C3, C5 and brakes B1 and B2. In forming the fourth forward speed, the clutch C2 causes the three rotating elements of the second planetary gear 22 (the second sun gear 22s, the second carrier 22c, and the second ring gear 22r, that is, the fourth rotating element, the fifth rotating element, and the second rotating gear). 6 rotation elements) are connected together. In addition, the first ring gear 21r (second rotating element) of the first planetary gear 21 and the second ring gear 22r (sixth rotating element) of the second planetary gear 22, that is, the output shaft 22o, cause the third gear train G3 by the clutch C4. Are connected to each other. In the present embodiment, the gear ratio γ4 at the fourth forward speed is γ4 = 2.000. The step ratio between the third forward speed and the fourth forward speed is γ3 / γ4 = 1.226.

  The fifth forward speed is formed by engaging the clutches C3 and C4 and disengaging the remaining clutches C1, C2, C5 and brakes B1 and B2. When the fifth forward speed is established, the clutch C3 causes the first sun gear 21s (first rotating element) of the first planetary gear 21, that is, the input shaft 20i and the second sun gear 22s (fourth rotating element) of the second planetary gear 22. Are connected to each other via the second gear train G2. In addition, the first ring gear 21r (second rotating element) of the first planetary gear 21 and the second ring gear 22r (sixth rotating element) of the second planetary gear 22, that is, the output shaft 22o, cause the third gear train G3 by the clutch C4. Are connected to each other. In the present embodiment, the gear ratio γ5 at the fifth forward speed is γ5 = 1.824. The step ratio between the fourth forward speed and the fifth forward speed is γ4 / γ5 = 1.097.

  The sixth forward speed is formed by engaging the clutches C2 and C3 and disengaging the remaining clutches C1, C4, C5 and the brakes B1 and B2. When forming the sixth forward speed, the clutch C2 causes the three rotating elements of the second planetary gear 22 (the second sun gear 22s, the second carrier 22c, and the second ring gear 22r, that is, the fourth rotating element, the fifth rotating element, and the second rotating gear). 6 rotation elements) are connected together. In addition, the first sun gear 21s (first rotating element) of the first planetary gear 21, that is, the input shaft 20i and the second sun gear 22s (fourth rotating element) of the second planetary gear 22 define the second gear train G2 by the clutch C3. Are connected to each other. In the present embodiment, the gear ratio γ6 at the sixth forward speed is γ6 = 1.550. The step ratio between the fifth forward speed and the sixth forward speed is γ5 / γ6 = 1.176.

  The seventh forward speed is formed by engaging the clutches C1 and C4 and disengaging the remaining clutches C2, C3, C5 and the brakes B1 and B2. In forming the seventh forward speed, the clutch C1 causes the three rotating elements of the first planetary gear 21 (the first sun gear 21s, the first ring gear 21r, and the first carrier 21c, that is, the first rotating element, the second rotating element, and the second rotating element). 3 rotation elements) are connected together. In addition, the first ring gear 21r (second rotating element) of the first planetary gear 21 and the second ring gear 22r (sixth rotating element) of the second planetary gear 22, that is, the output shaft 22o, cause the third gear train G3 by the clutch C4. Are connected to each other. In the present embodiment, the gear ratio γ7 at the seventh forward speed is γ7 = 1.250. The step ratio between the sixth forward speed and the seventh forward speed is γ6 / γ7 = 1.240.

  The eighth forward speed is formed by engaging the clutches C1 and C2 and releasing the remaining clutches C3 to C5 and the brakes B1 and B2. When forming the eighth forward speed, the clutch C1 causes the three planetary gears 21 to rotate (the first sun gear 21s, the first ring gear 21r, and the first carrier 21c, that is, the first rotation element, the second rotation element, and the second rotation element). 3 rotation elements) are connected together. Further, the clutch C2 brings together the three rotating elements of the second planetary gear 22 (the second sun gear 22s, the second carrier 22c, and the second ring gear 22r, that is, the fourth rotating element, the fifth rotating element, and the sixth rotating element). Connected. In the present embodiment, the gear ratio γ8 at the eighth forward speed is γ8 = 1.000. The step ratio between the seventh forward speed and the eighth forward speed is γ7 / γ8 = 1.250.

  The ninth forward speed is formed by engaging the clutches C1 and C3 and disengaging the remaining clutches C2, C4, C5 and brakes B1 and B2. In forming the ninth forward speed, the clutch C1 causes the three planetary gears 21 to rotate (the first sun gear 21s, the first ring gear 21r, and the first carrier 21c, that is, the first rotation element, the second rotation element, and the second rotation element). 3 rotation elements) are connected together. In addition, the first sun gear 21s (first rotating element) of the first planetary gear 21, that is, the input shaft 20i and the second sun gear 22s (fourth rotating element) of the second planetary gear 22 define the second gear train G2 by the clutch C3. Are connected to each other. In the present embodiment, the gear ratio γ9 at the ninth forward speed is γ9 = 0.849. The step ratio between the eighth forward speed and the ninth forward speed is γ8 / γ9 = 1.177.

  The tenth forward speed is formed by engaging the clutch C1 and the brake B2 and releasing the remaining clutches C2 to C5 and the brake B1. In forming the tenth forward speed, the clutch C1 causes the three rotating elements of the first planetary gear 21 (the first sun gear 21s, the first ring gear 21r, and the first carrier 21c, that is, the first rotating element, the second rotating element, and the first rotating gear). 3 rotation elements) are connected together. Further, the second sun gear 22s (fourth rotating element) of the second planetary gear 22 is fixed to the transmission case 11 so as not to rotate by the brake B2. In the present embodiment, the gear ratio γ10 at the tenth forward speed is γ10 = 0.667. The step ratio between the ninth forward speed and the tenth forward speed is γ9 / γ10 = 1.274.

  The reverse speed is formed by engaging the clutch C3 and the brake B1 and releasing the remaining clutches C1, C2, C4, C5 and the brake B2. In forming the reverse gear, the first sun gear 21s (first rotating element) of the first planetary gear 21, that is, the input shaft 20i and the second sun gear 22s (fourth rotating element) of the second planetary gear 22 are moved by the clutch C3. They are connected to each other via a two gear train G2. Further, the first carrier 21c (third rotating element) of the first planetary gear 21 and the second carrier 22c (fifth rotating element) of the second planetary gear 22 are fixed to the transmission case 11 so as not to rotate by the brake B1. The In this embodiment, the gear ratio γrev at the reverse speed is γrev = -3.100. The step ratio between the first forward speed and the reverse speed is | γrev / γ1 | = 0.620.

  In the automatic transmission 10 capable of forming the forward speed and the reverse speed from the first speed to the tenth speed, the spread sp from the lowest speed to the highest speed (gear ratio γ1 / forward 10 of the first speed) The gear ratio γ10) of the fast gear is sp = 7.500.

  Thus, in the automatic transmission 10 of the present embodiment, the forward speed and the reverse speed from the first speed stage to the tenth speed stage can be formed by engaging and disengaging the clutches C1 to C5 and the brakes B1 and B2. Here, the clutch C3 (first engagement element) that is engaged when the forward speed and the reverse speed of the fifth, sixth, and ninth speed stages are formed is the first sun gear 21s ( The first rotation element) and the second sun gear 22s (fourth rotation element) of the second planetary gear 22 are connected to each other via a gear train G2. At this time, the gear train G2 has a gear ratio gr2 of gr2. = 1.550 functions as a reduction gear. The clutch C4 (second engagement element) that is engaged when the first to fifth speed stages and the seventh forward speed are formed is the first ring gear 21r (second rotation) of the first planetary gear 21. Element) and the second ring gear 22r (sixth rotating element) of the second planetary gear 22 are connected to each other via a gear train G3. The gear train G3 at this time has a gear ratio gr3 of gr3 = 1. It functions as a 250 reduction gear. If one of the three rotating elements is an input element, the other one is a fixable element that can be fixed by a brake, and the other one is an output element, the planetary gear is input to the input element. It is possible to function as a reduction gear or a speed-up gear that reduces or speeds up the power to be transmitted to the output element. However, the addition of such planetary gears increases the axial length of the automatic transmission. The automatic transmission 10 according to the present embodiment replaces the planetary gear and the brake with a gear train (second and third gear trains G2 and G3) and a clutch (clutch C3 and C4), thereby reducing the planetary gear and the brake. Since two planetary gears can be omitted as compared with the above-described configuration, the axial length can be further shortened.

  In addition, in the automatic transmission 20 of the present embodiment, the third gear train G3 is disposed on the radially outer side of the first ring gear 21r of the first planetary gear 21, and the second planetary gear 22 is parallel to the input shaft 20i. The axial length can be further shortened by arranging it on the same axis as the counter shaft 40 (second axis) arranged in (1).

  According to the automatic transmission 20 of the present embodiment described above, the forward speed and the reverse speed from the first speed to the tenth speed can be formed by engaging / disengaging the clutches C1 to C5 and the brakes B1 and B2. it can. In the automatic transmission 20, the first carrier 21c (third rotating element) of the first planetary gear 21 and the second carrier 22c (fifth rotating element) of the second planetary gear 22 are connected to the first gear having a gear ratio gr1. The first sun gear 21s (first rotating element) of the first planetary gear 21 and the second sun gear 22s (fourth rotating element) of the second planetary gear 22 are connected to each other by the clutch C3 while being always connected via the row G1. The first ring gear 21r (second rotating element) of the first planetary gear 21 and the second ring gear 22r (sixth rotating element) of the second planetary gear 21 can be connected to each other via the second gear train G2 of gr2. Are connected to each other via a third gear train G3 having a gear ratio gr3. That is, the automatic transmission 20 according to the present embodiment causes the second gear train G2 and the clutch C3 to function as a reduction gear with a gear ratio gr2, and the third gear train G3 and the clutch C4 to function as a reduction gear with a gear ratio gr3. Two planetary gears can be omitted as compared with a configuration in which the reduction gear is constituted by a planetary gear and a brake. As a result, the automatic transmission 20 of the present embodiment can further reduce the shaft length while increasing the number of shift stages. Further, in the automatic transmission 20 of the present embodiment, the second planetary gear 22 can be disposed coaxially with the output shaft 20o (counter shaft 40) disposed in parallel with the input shaft 20i, and the axial length can be further increased. It can be shortened. In addition, since the automatic transmission 20 of the present embodiment arranges the third gear train G3 on the radially outer side of the first ring gear 21r of the first planetary gear 21, the axial length can be further shortened.

  FIG. 4 is a schematic configuration diagram of a power transmission device including a modified automatic transmission. An automatic transmission 20B in the power transmission device 10B shown in FIG. 4 is obtained by replacing the double pinion type first planetary gear 21 provided in the automatic transmission 20 of the present embodiment with a single pinion type first planetary gear 21B. is there. The single pinion type first planetary gear 21B includes a first sun gear 21s (first rotating element) that is an external gear, and a first ring gear 21r (first gear) that is an internal gear arranged concentrically with the first sun gear 21s. 3 rotation elements) and a first carrier 21c (second rotation element) holding a plurality of pinion gears 21p meshing with the first sun gear 21s and the first ring gear 21r so as to be rotatable (rotatable) and revolved. The first sun gear 21s of the first planetary gear 21B is always connected to the input shaft 20i, the first carrier 21c is always connected to the third drive gear 45 of the third gear train G3, and the first ring gear 21r is the first ring gear 21r. It is always connected to the first drive gear 41 of the gear train G1. The clutch C1 is configured to connect the first sun gear 21s and the first ring gear 21r of the first planetary gear 21B to each other and to release the connection between them, and the brake B1 is a first ring gear of the first planetary gear 21B. 21r and the transmission case 11 are connected to each other and the connection between them is released. The first planetary gear 21B has a gear ratio λ1 (the number of teeth of the first sun gear 21s / the number of teeth of the first ring gear 21r), for example, λ1 = 0.333. As a result, the first planetary gear 21B is changed from the order of the first sun gear 21s, the first ring gear 21r, and the first carrier 21c to the order of the first sun gear 21s, the first carrier 21c, and the first ring gear 21r. Thus, a speed diagram similar to that of the automatic transmission 20 of the present embodiment is established. Therefore, the automatic transmission 20B configured as described above can achieve the same effects as the automatic transmission 20 of the present embodiment. In the modified automatic transmission 20B, the first gear train G1 (the first drive gear 41 and the first driven gear 42) is disposed on the radially outer side of the first ring gear 21r of the first planetary gear 21B. Also good. Thereby, the axial length of the automatic transmission 20B can be further shortened.

  FIG. 5 is a schematic configuration diagram of a power transmission device including a modified automatic transmission. An automatic transmission 20C in the power transmission device 10C shown in FIG. 5 is obtained by replacing the single pinion type second planetary gear 22 included in the automatic transmission 20 of the present embodiment with a double pinion type second planetary gear 22C. is there. The second planetary gear 22C of the double pinion type is a second sun gear 22s (fourth rotating element) that is an external gear, and a second ring gear 22r (second gear) that is an internal gear arranged concentrically with the second sun gear 22s. And a plurality of pairs of two pinion gears 22pa and 22pb, one of which meshes with each other and one meshes with the second sun gear 22s and the other meshes with the second ring gear 22r. 2 carriers 22c (sixth rotating element). The second sun gear 22s of the second planetary gear 22C is always connected to the second driven gear 44 of the second gear train G2 via the counter shaft 40, and the second carrier 22c is always connected to the output shaft 20o, and the second ring gear. 22r is always connected to the first carrier 21c of the first planetary gear 21 via the gear train G1. The clutch C2 is configured to connect the second sun gear 22s and the second carrier 22c of the second planetary gear 22C to each other and to release the connection between them. The clutch C4 is configured to release the first ring gear of the first planetary gear 21. 21r and the carrier 22c of the second planetary gear 22 are connected to each other via a gear train G3 and are disconnected from each other. The second planetary gear 22C is configured such that the gear ratio λ2 (the number of teeth of the second sun gear 22s / the number of teeth of the second ring gear 22r) is, for example, λ2 = 0.333. Thus, the second planetary gear 22C is changed from the order of the second sun gear 22s, the second carrier 22c, and the second ring gear 22r to the order of the second sun gear 22s, the second ring gear 22r, and the second carrier 22c. Thus, a speed diagram similar to that of the automatic transmission 20 of the present embodiment is established. Therefore, the automatic transmission 20 </ b> C configured as described above can achieve the same effects as the automatic transmission 20 of the present embodiment. Further, the automatic transmission 20C is configured to be arranged in the order of the first gear train G1, the third gear train G3, and the second gear train G2 in the axial direction from the fluid transmission device 12 side. Each gear train is configured such that the gear ratio gr1 of the first gear train G1 is the smallest and the gear ratio gr2 of the second gear train G2 is the largest, so that the three gear trains G1 to G3 are the fluid transmission device 12. Are arranged in order of increasing gear ratio, that is, in order of increasing outer diameter of the drive gear. Therefore, it is possible to further improve the assemblability when the three gear trains G1 to G3 are assembled in order in the axial direction.

  In the automatic transmission 20 according to the present embodiment, the clutch C1 connects the first sun gear 21s and the first carrier 21c of the first planetary gear 21 to each other and releases the connection between them. The first sun gear 21s and the first ring gear 21r may be connected to each other and the connection between the first sun gear 21s and the first ring gear 21r may be released, or the first carrier 21c and the first ring gear 21r of the first planetary gear 21 may be connected to each other. It is good also as what cancels | releases both connection. That is, the clutch C1 only needs to connect any two of the three rotating elements of the first planetary gear 21 to each other and release the connection between them.

  In the automatic transmission 20 of the present embodiment, the clutch C2 connects the second sun gear 22s and the second carrier 22c of the second planetary gear 22 to each other and releases the connection between them. The second sun gear 22s and the second ring gear 22r may be connected to each other and the connection between them may be released, or the second carrier 22c of the second planetary gear 22 and the second ring gear 22r may be connected to each other. It is good also as what cancels | releases both connection. That is, the clutch C2 only needs to connect any two of the three rotating elements of the second planetary gear 22 to each other and release the connection therebetween.

  In the automatic transmission 20 of the present embodiment, the clutch C3 connects the first sun gear 21s of the first planetary gear 21 (the first rotating element of the first planetary gear) and the second drive gear 43 of the second gear train G2 to each other. Although the connection and the connection between the two are released, the second driven gear 44 of the second gear train G2 and the second sun gear 22s of the second planetary gear 22 (fourth rotating element of the second planetary gear) are connected to each other. In addition, the connection between the two may be canceled.

  In the automatic transmission 20 of the present embodiment, the clutch C4 connects the third driven gear 46 of the third gear train G3 and the second ring gear 22r of the second planetary gear 22 (sixth rotating element of the second planetary gear) to each other. However, the third drive gear 45 of the third gear train G3 and the first ring gear 21r of the first planetary gear 21 (the second rotating element of the first planetary gear) are connected to each other. In addition, the connection between the two may be canceled. That is, the clutch C4 is not limited to be disposed coaxially with the counter shaft 40 (second shaft), and may be disposed coaxially with the input shaft 20i (first shaft).

  In the automatic transmission 20 of the present embodiment, the clutch C1 to C5 and the brakes B1 and B2 are configured to be able to form the forward speed and the reverse speed from the first speed to the tenth speed, but the clutch C5 May be omitted. In this case, the gear ratio of the third gear shown in FIG. 3 is omitted, and the forward gear from the first gear to the ninth gear can be formed.

  In the automatic transmission 20 of the present embodiment, the first drive gear 41 (the first carrier 21c of the first planetary gear 21) of the first gear train G1 is fixed to the transmission case 11 so as not to rotate, and the first drive gear. 41, the first driven gear 42 (the second planetary gear carrier 22c) of the first gear train G1 is fixed to the transmission case 11 so as not to rotate, and the first driven gear 42 is fixed to the transmission case 11. 42 may be released from being fixed to the transmission case 11. That is, the brake B1 is not limited to the one arranged coaxially with the input shaft 20i (first axis), and may be arranged coaxially with the counter shaft 40 (second axis).

  In the automatic transmission 20 of the present embodiment, the second drive gear 43 of the second gear train G2 is fixed to the transmission case 11 so as not to rotate, and the second drive gear 43 is released from being fixed to the transmission case 11. However, the second driven gear 44 (counter shaft 40) of the second gear train G2 may be fixed to the transmission case 11 so as not to rotate, and the second driven gear 44 may be released from being fixed to the transmission case 11. That is, the brake B2 is not limited to the one arranged coaxially with the input shaft 20i (first axis), and may be arranged coaxially with the counter shaft 40 (second axis).

  As described above, the automatic transmission according to the present disclosure shifts the power input to the input shaft (20i) to a plurality of shift speeds and outputs the output shaft (20o) arranged in parallel to the input shaft (20i). A first planetary gear (21) having three rotation elements (21s, 21r, 21c) arranged coaxially with the input shaft (20i), A third rotary element (22s, 22r, 22c) arranged coaxially with the shaft (20o), and the output shaft (20o) is always connected to any one of the three rotary elements (22r). Two planetary gears (22), a first drive gear (41) and a first driven gear (42) meshing with each other, and the first drive gear (41) is rotated three times by the first planetary gear (21). A predetermined rotating element (21c) of the elements; A first gear train (G1) that is connected when the first driven gear (42) is always connected to a predetermined one of the three rotating elements (22c) of the second planetary gear (22); The second drive gear (43) and the second driven gear (44) meshing with each other, the second gear train (G2) having a gear ratio different from that of the first gear train (G1), and the third drive gear meshing with each other (45) and a third driven gear (46), the third gear train (G3) having a gear ratio different from that of the first gear train (G1) and the second gear train (G2), and the first planetary gear. The other rotating element (21s) different from the one rotating element (21c) of (21) and the other rotating element (22s) different from the one rotating element (22c) of the second planetary gear (22). And the second drive gear (43) and the second A first engagement element (C3) that connects to each other via a driven gear (44) and releases the connection therebetween, the one rotation element (21c) of the first planetary gear (21), and the other rotation element The remaining rotating element (21r) different from (21s) and the remaining rotating element (22r) different from the one rotating element (22c) and the other rotating element (22s) of the second planetary gear (22). And a second engagement element (C4) for releasing the connection between the third drive gear (45) and the third driven gear (46). is there.

  According to the automatic transmission of the present disclosure, the first planetary gear (21) and the output shaft (20o) arranged in parallel with the input shaft (20i) are always connected to any one of the three rotating elements. A second planetary gear (22); first, second and third gear trains (G1, G2, G3) having different gear ratios; and first and second engagement elements (C3, C4). Composed. Then, the first gear train (G1) is set to a predetermined one of the three rotation elements of the first planetary gear (21) and one of the three rotation elements of the second planetary gear (22). The first engaging element (C3) is connected to the other rotating element (21s) of the first planetary gear (21) and the second planetary gear (22). ) And the other rotating element (22s) are connected to each other via the second gear train (G2) and disconnected from each other, and the second engaging element (C4) is connected to the first planetary gear ( 21) The remaining rotating element (21r) of 21) and the remaining rotating element (22r) of the second planetary gear (22) are connected to each other via the third gear train (G3) and are disconnected from each other. To do. As a result, the first engagement element (C3) and the second gear train (G2), and the second engagement element (C4) and the third gear train (G3) are reduced at different gear ratios. It can function as a gear or a speed-up gear. Therefore, in the automatic transmission according to the present disclosure, two planetary gears can be omitted as compared with the configuration in which the reduction gear or the speed increasing gear is configured using the planetary gear and the engagement element (brake). The first planetary gear (21) is arranged coaxially with the input shaft (20i), while the second planetary gear (22) is arranged with an output shaft (20o) arranged in parallel with the input shaft (20i). Since it is arranged coaxially, the axial length is shorter than that in which two planetary gears are arranged coaxially with the input shaft. As a result, the shaft length of the automatic transmission can be further shortened while making it possible to increase the number of shift stages.

  In the automatic transmission according to the present disclosure, the input shaft may be always connected to the other rotating element (21s) of the first planetary gear (21).

  Further, in the automatic transmission according to the present disclosure, a third engagement element (C1) that connects any two rotation elements (21s, 21c) of the first planetary gear (21) to each other and releases the connection therebetween. And a fourth engagement element (C2) for connecting any two rotation elements (22s, 22c) of the second planetary gear (22) to each other and releasing the connection therebetween. .

  Furthermore, in the automatic transmission according to the present disclosure, of the three rotating elements of the first planetary gear (21), the rotating element (21c) to which the input shaft (20i) is not always connected is connected to the stationary member (11). Thus, the output shaft (20o) is always connected among the three rotating elements of the second planetary gear (22) and the fifth engaging element (B1) that is fixed to be non-rotatable and releases the connection therebetween. A non-rotating element (22s) connected to the stationary member (11) is fixed to be non-rotatable, and a sixth engaging element (B2) that releases the connection of both is also provided.

  In the automatic transmission of the present disclosure, the output shaft (20o) is always coupled to the remaining rotating element (22r) of the second planetary gear (22) to which the third driven gear (46) is connected, A seventh engagement element (C5) for connecting the first drive gear (41) and the second drive gear (43) to each other and releasing the connection between them may be provided. If it carries out like this, when the output shaft (20o) rotates, the rotation element (22c) connected with the 1st driven gear (42) of the 2nd planetary gear (22) and the rotation connected with the 2nd driven gear (44). A rotational speed difference corresponding to the gear ratio of the first and second gear trains (G1, G2) can be generated between the element (22s). As a result, the seventh engagement element (C5) can be provided to further increase the speed.

  In the automatic transmission according to the present disclosure, the first planetary gear (21) includes a first rotating element (21s) that is the other rotating element and a second rotating element that is the remaining rotating element in the velocity diagram. (21r) and the third rotating element (21c) that is the one rotating element, and the second planetary gear (22) is a fourth rotating element that is the other rotating element in the velocity diagram. The rotation element (22s), the fifth rotation element (22c) as the one rotation element, and the sixth rotation element (22r) as the remaining rotation element are arranged in this order, and the input shaft (20i) Is always connected to the first rotating element (21s) of the first planetary gear (21), and the output shaft (20o) is always connected to the sixth rotating element (22r) of the second planetary gear (22). And the first gear train (G1) Always connected to the third rotating element (21c) of the gear (21) and the fifth rotating element (22c) of the second planetary gear (22), the first engaging element (C3) is connected to the first planetary gear (22). The first rotating element (21s) of the gear (21) and the fourth rotating element (22s) of the second planetary gear (22) are connected to each other via the second gear train (G2) and are connected to each other. The second engagement element (C4) releases the second rotation element (21r) of the first planetary gear (21) and the sixth rotation element (22r) of the second planetary gear (22). It is also possible to connect to each other via the third gear train (G3) and to release the connection between them.

  As mentioned above, although the embodiment of the invention of the present disclosure has been described, the invention of the present disclosure is not limited to such an embodiment and can be implemented in various forms without departing from the gist of the invention of the present disclosure. Of course you can.

  The invention of the present disclosure can be used in the manufacturing industry of automatic transmissions.

  10, 10B, 10C power transmission device, 11 transmission case, 12 fluid transmission device, 20, 20B, 20C automatic transmission, 20i input shaft, 20o output shaft, 21, 21B first planetary gear, 21s first sun gear, 21r first 1 ring gear, 21c first carrier, 21pa, 21pb pinion gear, 22, 22C second planetary gear, 22s second sun gear, 22r second ring gear, 22c second carrier, 22p pinion gear, 40 counter shaft, 41 first drive gear, 42 1st driven gear, 43 2nd drive gear, 44 2nd driven gear, 45 3rd drive gear, 46 3rd driven gear, B1, B2 brake, C1-C5 clutch, G1 1st gear train, G2 2nd gear train, G3 1st 3 gear trains.

Claims (6)

An automatic transmission that shifts power input to an input shaft to a plurality of shift speeds and outputs the power to an output shaft arranged in parallel to the input shaft,
A first planetary gear having three rotating elements arranged coaxially with the input shaft;
A second planetary gear having three rotating elements arranged coaxially with the output shaft, the output shaft being always connected to any of the three rotating elements;
A first drive gear and a first driven gear meshing with each other, wherein the first drive gear is always connected to a predetermined one of the three rotating elements of the first planetary gear, and the first driven gear is A first gear train always connected to a predetermined one of the three rotating elements of the second planetary gear;
A second gear train including a second drive gear and a second driven gear meshing with each other, and having a gear ratio different from that of the first gear train;
A third gear train including a third drive gear and a third driven gear meshing with each other, and having a gear ratio different from that of the first gear train and the second gear train;
The second drive gear and the second driven gear are connected to another rotation element different from the one rotation element of the first planetary gear and another rotation element different from the one rotation element of the second planetary gear. A first engaging element that connects to each other and releases the connection between the two,
A remaining rotating element different from the one rotating element and the other rotating element of the first planetary gear and a remaining rotating element different from the one rotating element and the other rotating element of the second planetary gear; Are connected to each other via the third drive gear and the third driven gear, and a second engagement element for releasing the connection between them,
An automatic transmission comprising: The automatic transmission according to claim 1,
The input shaft is always connected to the other rotating element of the first planetary gear,
Automatic transmission. The automatic transmission according to claim 1 or 2,
A third engaging element that connects any two rotating elements of the first planetary gear and releases the connection between the two rotating elements;
A fourth engaging element for connecting any two rotating elements of the second planetary gear to each other and releasing the connection between the two rotating elements;
An automatic transmission comprising: The automatic transmission according to any one of claims 1 to 3,
A fifth engaging element for connecting the rotating element, to which the input shaft is not always connected, of the three rotating elements of the first planetary gear to a stationary member and fixing the non-rotatable and releasing the connection between them;
A sixth engaging element for connecting the rotating element, to which the output shaft is not always connected, of the three rotating elements of the second planetary gear to a stationary member to fix the non-rotatable and to release the connection between them;
An automatic transmission comprising: The automatic transmission according to any one of claims 1 to 4,
The output shaft is always coupled to the remaining rotating element of the second planetary gear to which the third driven gear is connected,
An automatic transmission comprising a seventh engagement element that connects the first drive gear and the second drive gear to each other and releases the connection therebetween. The automatic transmission according to any one of claims 1 to 5,
In the velocity diagram, the first planetary gear is arranged in the order of the first rotating element that is the other rotating element, the second rotating element that is the remaining rotating element, and the third rotating element that is the one rotating element. Formed as
In the velocity diagram, the second planetary gear is arranged in the order of the fourth rotating element that is the other rotating element, the fifth rotating element that is the one rotating element, and the sixth rotating element that is the remaining rotating element. Formed as
The input shaft is always connected to the first rotating element of the first planetary gear;
The output shaft is always connected to the sixth rotating element of the second planetary gear;
The first gear train is always connected to a third rotating element of the first planetary gear and a fifth rotating element of the second planetary gear;
The first engagement element connects the first rotation element of the first planetary gear and the fourth rotation element of the second planetary gear to each other via the second gear train and releases the connection between the two,
The second engaging element connects the second rotating element of the first planetary gear and the sixth rotating element of the second planetary gear to each other via the third gear train and automatically releases the connection between them. transmission.

Images