JP2014035056A - Automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a novel automatic transmission comprising four planetary gear mechanisms, four clutches and two brakes, and to improve transfer efficiency of power.SOLUTION: An automatic transmission includes four planetary gear mechanisms P1, P2, P3, P4 of a single pinion type, and in the automatic transmission, a sun gear P11 and a sun gear P41 are connected by a connection element R1, a ring gear P23, a carrier P32 and a carrier R42 are connected by a connection element R2, and a ring gear P33 and a ring gear P43 are connected by a connection element R3; a ring gear P13 and the connection element R3 are connected by a clutch C1, a carrier P12 and the connection element R3 are connected by a clutch C2, a carrier 22 and a sun gear P31 are connected by a clutch C3, and a sun gear P21 and the sun gear P31 are connected by a clutch C4; the ring gear P13 and the sun gear P21 are connected to a case 2 by brakes B1, B2; an input shaft 3 is connected to the carrier P22; and an output shaft 4 is connected to the carrier P12. Consequently, the automatic transmission has a constitution capable of changing speed to 10 advance speed stages and an astern stage.

Description

  The present invention relates to an automatic transmission apparatus that shifts power input to an input member and outputs the power to an output member.

  Conventionally, as this type of automatic transmission device, one that can form a forward seventh speed and a reverse speed by using four planetary gear mechanisms, three clutches, and three brakes has been proposed (for example, patents). Reference 1). The configuration of this apparatus is shown in FIG. As shown in the drawing, a conventional automatic transmission device 901 as a background art includes one double-pinion planetary gear mechanism S1 and three single-pinion planetary gear mechanisms S2, S3, and S4. The planetary gear mechanism S1 is engaged with the sun gear S11 as an external gear, the ring gear S13 as an internal gear, a plurality of first pinion gears S14 that mesh with the sun gear S11, and the first pinion gear S14 and the ring gear S13. A plurality of second pinion gears S15 that mesh with each other, and a plurality of first pinion gears S14 and a carrier S12 that holds the plurality of second pinion gears S15 so as to rotate and revolve freely. The three planetary gear mechanisms S2, S3, S4 include sun gears S21, S31, S41 as external gears, ring gears S23, S33, S43 as internal gears, sun gears S21, S31, S41 and ring gears S23, S33, A plurality of pinion gears S24, S34, S44 meshing with S43, and carriers S22, S32, S42 that hold the plurality of pinion gears S24, S34, S44 so as to rotate and revolve freely. The carrier S22 of the planetary gear mechanism S2 and the ring gear S33 of the planetary gear mechanism S3 are connected by a connecting element T1, and the ring gear S23 of the planetary gear mechanism S2, the carrier S32 of the planetary gear mechanism S3, and the carrier S42 of the planetary gear mechanism S4 are connected. The sun gear S31 of the planetary gear mechanism S3 and the sun gear S41 of the planetary gear mechanism S4 are connected by a connecting element T3. The carrier S12 of the planetary gear mechanism S1 is connected to the coupling element T3 (sun gear S31, sun gear S41) via the clutch C1, and is connected to the coupling element T1 (carrier S22, ring gear S33) via the clutch C2. Yes. Further, the ring gear S13 of the planetary gear mechanism S1 is connected to the sun gear S21 of the planetary gear mechanism S2 via the clutch C3. The connecting element T1 (carrier S22, ring gear S33) is connected to the case 902 of the automatic transmission device 901 by the brake B1, and the ring gear S43 of the planetary gear mechanism S4 is connected to the case 902 by the brake B2. The sun gear S21 of the mechanism S2 is connected to the case 902 by the b input shaft 3. Further, the coupling element T1 (carrier S22, ring gear S33) is connected to the case 902 by a one-way clutch OWC. The input shaft 903 is connected to the carrier S12 of the planetary gear mechanism S1, and the output shaft 904 is connected to the coupling element T2 (ring gear S23, carrier S32, carrier S42).

  In this conventional automatic transmission device 901, the gear ratios λ1, λ2, λ3, λ4 of the planetary gear mechanisms S1, S, S3, S4 (the number of teeth of the sun gear / the number of teeth of the ring gear in each planetary gear mechanism) are 0. .544, 0.439, 0.310, and 0.535, and as shown in the operation table of FIG. 7, the first forward speed to the seventh forward speed and the reverse speed are formed as follows. . The first forward speed (gear ratio is 4.222) is formed by engaging the clutch C1 and the brake B1 and releasing the clutches C2 and C3 and the brakes B2 and B3. In 868, the step ratio (gear ratio of the first forward speed / gear ratio of the second forward speed) is 1.47). The clutch C1 and the brake B3 are engaged, and the clutches C2, C3 and the brakes B1, B2 are released. The third forward speed (the gear ratio is 1.979 and the step ratio (the gear ratio of the second forward speed / the gear ratio of the third forward speed) is 1.45) is engaged with the clutch C1 and the brake B2. In addition, it is formed by releasing the clutches C2 and C3 and the brakes B1 and B3, and the fourth forward speed (gear ratio is 1.369 and the step ratio (gear ratio of the third forward speed / gear ratio of the fourth forward speed)) 1 45) is formed by engaging the clutches C1 and C3 and releasing the clutch C2 and the brakes B1 to B3. The fifth forward speed (gear ratio is 1.000 and the step ratio (gear ratio of fourth forward speed / The fifth forward speed gear ratio) is 1.37) formed by engaging the clutches C1 and C2 and releasing the clutch C3 and the brakes B1 to B3. The sixth forward speed (gear ratio is 0.807). The step ratio (gear ratio of the fifth forward speed / gear ratio of the sixth forward speed) is 1.24) formed by engaging the clutches C2 and C3 and releasing the clutch C1 and the brakes B1 to B3. The seventh speed (the gear ratio is 0.695 and the step ratio (gear ratio of the sixth forward speed / gear ratio of the seventh forward speed) is 1.16) is engaged with the clutch C2 and the brake B2, and the clutches C1, C3 And The reverse gear (gear ratio is -5.004) is formed by engaging the clutch C3 and the brake B1 and releasing the clutch C1, C2 and the brake B2, B3. . In this conventional automatic transmission device 901, the gear ratio of the first forward speed of the lowest speed stage is 4.222 and the gear ratio of the seventh forward speed of the highest speed stage is 0.695. (Gear ratio of the lowest speed stage / gear ratio of the highest speed stage) is 6.06.

JP 2010-203536 A

  In such an automatic transmission device, when an automatic transmission is configured by four planetary gear mechanisms and six engaging elements, there are many ways to connect the rotating elements of the four planetary gear mechanisms and attach the six engaging elements. There are some that can function as an automatic transmission device and some that cannot function depending on the connection and installation. For this reason, it becomes difficult to find a connection or attachment method that functions as an automatic transmission device.

  The planetary gear mechanism constituting the automatic transmission device includes a single pinion type planetary gear mechanism and a double pinion type planetary gear mechanism. The double pinion type planetary gear mechanism includes two rows in the radial direction. Since the pinion gear is provided, the pinion gears mesh with each other, and the gear meshing loss increases and the power transmission efficiency decreases compared to the single pinion planetary gear mechanism. Further, since the double pinion type planetary gear mechanism has two rows of pinion gears in the radial direction, the number of parts is increased and the assembling property and the economical efficiency are also reduced as compared with the single pinion type planetary gear mechanism. For this reason, it is preferable that as many of the four planetary gear mechanisms that constitute the automatic transmission device be constituted by a single pinion type planetary gear mechanism.

  Further, in the automatic transmission device, if the gear ratio width (the gear ratio of the lowest speed stage / the gear ratio of the highest speed stage) is increased, both the fuel consumption and acceleration of the vehicle to be mounted can be achieved. A larger width is preferred. On the other hand, if the step ratio (the gear ratio of one gear position on the low speed side / the gear ratio of the gear stage) is large, smooth acceleration before and after the gear shift is impaired. For this reason, in the automatic gear ratio device, in order to increase the gear ratio width with a step ratio within an appropriate range, it is preferable that the number of forward gears is large.

  Further, even if the engagement element of the automatic transmission device is released, drag loss due to slight contact occurs. Therefore, if there are many engagement elements that are released when the shift stage is formed, power transmission efficiency due to drag loss. Will fall. For this reason, in the automatic transmission device, it is preferable that fewer engagement elements are released when each gear stage is formed.

  The automatic transmission apparatus of the present invention is mainly intended to propose a new automatic transmission apparatus having four planetary gear mechanisms and six engagement elements, and further to improve power transmission efficiency. With the purpose.

  The automatic transmission apparatus of the present invention employs the following means in order to achieve at least the above-described main object.

The automatic transmission device of the present invention is
An automatic transmission device that shifts the power input to the input member and outputs it to the output member,
A planetary gear mechanism P1 having a rotation element P11, a rotation element P12, and a rotation element P13 in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
A planetary gear mechanism P2 having a rotation element P21, a rotation element P22, and a rotation element P23 in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
A planetary gear mechanism P3 having a rotating element P31, a rotating element P32, and a rotating element P33 in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
A planetary gear mechanism P4 having a rotation element P41, a rotation element P42, and a rotation element P43 in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
A connecting element R1 that connects the rotating element P11 and the rotating element P41;
A connecting element R2 that connects the rotating element P23, the rotating element P32, and the rotating element P42;
A connecting element R3 that connects the rotating element P33 and the rotating element P43;
A clutch C1 that engages the rotation element P13 and the coupling element R3 and releases the engagement;
A clutch C2 that engages and disengages the rotating element P12 and the connecting element R3;
A clutch C3 for engaging and releasing the rotation element P22 and the rotation element P31;
A clutch C4 for engaging and releasing the rotation element P21 and the rotation element P31;
A brake B1 that engages the rotating element P13 in a fixed manner with an automatic transmission device case and releases the engagement;
A brake B2 for engaging the rotating element P21 with the automatic transmission device case in a fixable manner and releasing the engagement;
With
Connecting the input member to the rotating element P22;
The output member is connected to the rotating element P12.
It is characterized by that.

  In the automatic transmission device according to the present invention, the planetary gear mechanism P1 having the rotation element P11, the rotation element P12, and the rotation element P13 in the arrangement order at intervals corresponding to the gear ratio in the speed diagram, and the gear ratio in the speed diagram. , The planetary gear mechanism P2 having the rotation element P21, the rotation element P22, and the rotation element P23 in the arrangement order at intervals corresponding to each other, and the rotation element P31 and the rotation element P32 in the arrangement order at intervals corresponding to the gear ratio in the velocity diagram. A planetary gear mechanism P3 having a rotation element P33, and a planetary gear mechanism P4 having a rotation element P41, a rotation element P42, and a rotation element P43 in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram. The element P11 and the rotating element P41 are connected by the connecting element R1, and the rotating element P23, the rotating element P32, and the rotating element P42 are connected by the connecting element R2. And it is connected by a connecting element R3 to the rotation element P33 and the rotation element P43. Further, the rotating element P13 and the connecting element R3 are connected via the clutch C1, the rotating element P12 and the connecting element R3 are connected via the clutch C2, and the rotating element P22 and the rotating element P31 are connected via the clutch C3. The rotary element P21 and the rotary element P31 are connected via the clutch C4. Further, the rotating element P13 is connected to the automatic transmission device case by the brake B1, and the rotating element P21 is connected to the automatic transmission device case by the brake B2. Then, the input member is connected to the rotation element P22, and the output member is connected to the rotation element P12. Thus, an automatic transmission that can function by the four planetary gear mechanisms, the four clutches, and the two brakes can be configured.

In such an automatic transmission apparatus according to the present invention, the first forward speed to the tenth forward speed and the reverse speed can be configured as follows.
(1) The first forward speed is established by engaging the clutch C3, the brake B1, and the brake B2, and releasing the clutch C1, the clutch C2, and the clutch C4.
(2) The second forward speed is formed by engaging the clutch C2, the clutch C3, and the brake B1, and releasing the clutch C1, the clutch C4, and the brake B2.
(3) The third forward speed is formed by engaging the clutch C2, the clutch C4, and the brake B1, and releasing the clutch C1, the clutch C3, and the brake B2.
(4) The fourth forward speed is established by engaging the clutch C1, the clutch C4, and the brake B1, and releasing the clutch C2, the clutch C3, and the brake B2.
(5) The fifth forward speed is formed by engaging the clutch C1, the clutch C2, and the clutch C4 and releasing the clutch C3, the brake B1, and the brake B2.
(6) The sixth forward speed is established by engaging the clutch C1, the clutch C4, and the brake B2 and releasing the clutch C2, the clutch C3, and the brake B1.
(7) The seventh forward speed is formed by engaging the clutch C1, the clutch C3, and the brake B2 and releasing the clutch C2, the clutch C4, and the brake B1.
(8) The eighth forward speed is formed by engaging the clutch C1, the clutch C2, and the brake B2 and releasing the clutch C3, the clutch C4, and the brake B1.
(9) The ninth forward speed is established by engaging the clutch C2, the clutch C3, and the brake B2 and releasing the clutch C1, the clutch C4, and the brake B1.
(10) The tenth forward speed is formed by engaging the clutch C2, the clutch C4, and the brake B2, and releasing the clutch C1, the clutch C3, and the brake B1.
(11) The reverse gear is formed by engaging the clutch C4, the brake B1, and the brake B2 and releasing the clutch C1, the clutch C2, and the clutch C3.
If it carries out like this, it can be set as the apparatus which can carry out gear shifting from the 1st forward speed to the 10th forward speed and the reverse speed by four planetary gear mechanisms, four clutches, and two brakes. As a result, the automatic transmission apparatus of the present invention has a larger number of forward shift stages than the conventional automatic transmission apparatus capable of shifting from the first forward speed to the seventh forward speed and the reverse speed. Compared to the conventional automatic transmission device, it is possible to improve the fuel efficiency while achieving both the fuel efficiency and acceleration of the vehicle mounted, and smooth acceleration before and after the shift. Can be held.

  As described above, any one of the first forward speed, the forward 10th speed stage, and the reverse speed stage engages three engagement elements among the six engagement elements including the four clutches and the two brakes. The automatic transmission device of the present invention engages two engagement elements among the six engagement elements and four engagement elements. The engagement elements to be released can be reduced as compared to the conventional automatic transmission device that releases the engagement. Even if the engagement elements are released, drag loss due to slight contact occurs. Therefore, if there are many engagement elements that are released when the shift stage is formed, power transmission efficiency is reduced due to drag loss. Since the automatic transmission device of the present invention has fewer engaging elements to be released compared to the conventional automatic transmission device, the power transmission efficiency is higher than that of the conventional automatic transmission device. Can be high.

  In the above-described automatic transmission device of the present invention, the planetary gear mechanism P1, the planetary gear mechanism P2, the planetary gear mechanism P3, and the planetary gear mechanism P4 each include a sun gear, a ring gear, and a carrier as the three rotating elements. The rotating element P11, the rotating element P21, the rotating element P31, and the rotating element P41 are all sun gears, and the rotating element P12 and the rotating element are configured as a single pinion planetary gear mechanism. P22, the rotating element P32, and the rotating element P42 are all carriers, and the rotating element P13, the rotating element P23, the rotating element P33, and the rotating element P43 are all ring gears. It can also be done. That is, all of the four planetary gear mechanisms are configured as a single pinion type planetary gear mechanism. Since the double pinion type planetary gear mechanism has two rows of pinion gears in the radial direction, the pinion gears mesh with each other, resulting in an increase in gear meshing loss and transmission of power compared to the single pinion type planetary gear mechanism. Efficiency is reduced. Further, since the double pinion type planetary gear mechanism has two rows of pinion gears in the radial direction, the number of parts is increased and the assembling property and the economical efficiency are also reduced as compared with the single pinion type planetary gear mechanism. By configuring all of the four planetary gear mechanisms of the automatic transmission device of the present invention as single-pinion type planetary gear mechanisms, three of the four planetary gear mechanisms are configured as single-pinion type planetary gear mechanisms. In addition, the power transmission efficiency can be increased and the assembly and economy can be improved as compared with the conventional automatic transmission device in which one is configured as a double pinion type planetary gear mechanism. Can do.

  In the automatic transmission device according to the present invention, the brake B1 may be configured as a dog brake. The dog brake is susceptible to shock when engaged, and synchronous control is required to synchronize the rotation. However, the brake B1 is continuously engaged from the first forward speed to the fourth forward speed, and from the fifth forward speed to the forward 10 speed. Since the release is continued up to the speed stage, the engagement and release are not repeated frequently, and the frequency of occurrence of the synchronous control is low. For this reason, even if the dog brake is employed, the deterioration of the shift feeling is suppressed.

It is a block diagram which shows the outline of a structure of the automatic transmission apparatus 1 of an Example. 3 is an operation table of the automatic transmission device 1. 3 is a speed diagram of the automatic transmission device 1. FIG. It is a block diagram which shows the outline of a structure of the automatic transmission apparatus 1B of a modification. It is a block diagram which shows the outline of a structure of the automatic transmission apparatus 1C of a modification. It is a block diagram which shows the outline of a structure of the automatic transmission apparatus 901 of a prior art example. It is an operation | movement table | surface of the automatic transmission apparatus 901 of a prior art example.

  Next, embodiments of the present invention will be described using examples.

  FIG. 1 is a block diagram showing an outline of the configuration of an automatic transmission device 1 as an embodiment of the present invention. The automatic transmission device 1 of the embodiment includes four single pinion planetary gear mechanisms P1, P2, P3, P4, four clutches C1, C2, C3, C4, and two brakes B1, B2. It is mounted on a vehicle (for example, front engine rear drive type) in which an engine (not shown) as an internal combustion engine is installed vertically (in the longitudinal direction of the vehicle), and the power from the engine is started by a torque converter (not shown). It is configured as a stepped transmission mechanism that inputs from an input shaft (input shaft) 3 through the device and shifts the input power to output it to an output shaft (output shaft) 4. The power output to the output shaft 4 is output to the left and right drive wheels via a differential gear (not shown). In the automatic transmission 1 of the embodiment, as shown in FIG. 1, the planetary gear mechanism P2, the planetary gear mechanism P3, the planetary gear mechanism P4, and the planetary gear mechanism P1 are arranged in this order from the input shaft 3 side.

  The planetary gear mechanism P1 includes a sun gear P11 as an external gear, a ring gear P13 as an internal gear disposed concentrically with the sun gear P11, and a plurality of pinion gears P14 that mesh with the sun gear P11 and mesh with the ring gear P13. And a carrier P12 that couples and holds the plurality of pinion gears P14 so as to rotate and revolve freely. Since the planetary gear mechanism P1 is configured as a single pinion type planetary gear mechanism, the three rotating elements, the sun gear P11, the ring gear P13, and the carrier P12, are arranged in an order corresponding to the gear ratio in the speed diagram. As shown, the sun gear P11, the carrier P12, and the ring gear P13 are obtained. The gear ratio λ1 (the number of teeth of the sun gear P11 / the number of teeth of the ring gear P13) of the planetary gear mechanism P1 is set to 0.40, for example.

  Similarly to the planetary gear mechanism P1, the planetary gear mechanism P2 is also configured as a single pinion type planetary gear mechanism. As the three rotating elements, a sun gear P21, a ring gear P23, and a plurality of pinion gears P24 are connected to rotate. And a carrier P22 that is held to revolve freely. The sun gear P21, the ring gear P23, and the carrier P22, which are the three rotating elements of the planetary gear mechanism P2, are the sun gear P21, the carrier P22, and the ring gear P23 when shown in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram. The gear ratio λ2 (the number of teeth of the sun gear P21 / the number of teeth of the ring gear P23) of the planetary gear mechanism P2 is set to 0.50, for example.

  The planetary gear mechanism P3 is also configured as a single pinion type planetary gear mechanism, like the planetary gear mechanism P1 and the planetary gear mechanism P2, and includes three rotation elements: a sun gear P31, a ring gear P33, and a plurality of pinion gears P34. And a carrier P32 that is rotatably and revolved. The sun gear P31, the ring gear P33, and the carrier P32, which are the three rotating elements of the planetary gear mechanism P3, become the sun gear P31, the carrier P32, and the ring gear P33 when shown in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram. The gear ratio λ3 (the number of teeth of the sun gear P31 / the number of teeth of the ring gear P33) of the planetary gear mechanism P3 is set to 0.45, for example.

  The planetary gear mechanism P4 is also configured as a single pinion type planetary gear mechanism, similar to the planetary gear mechanism P1, the planetary gear mechanism P2, and the planetary gear mechanism P3. The planetary gear mechanism P4 includes a sun gear P41, a ring gear P43, and three rotating elements. And a carrier P42 that couples and holds the plurality of pinion gears P44 so as to rotate and revolve freely. The sun gear P41, the ring gear P43, and the carrier P42, which are the three rotating elements of the planetary gear mechanism P4, become the sun gear P41, the carrier P42, and the ring gear P43 when shown in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram. The gear ratio λ4 (the number of teeth of the sun gear P41 / the number of teeth of the ring gear P43) of the planetary gear mechanism P4 is set to, for example, 0.30.

  The sun gear P11 of the planetary gear mechanism P1 and the sun gear P41 of the planetary gear mechanism P4 are connected by a connecting element R1, and the ring gear P23 of the planetary gear mechanism P2, the carrier P32 of the planetary gear mechanism P3, and the carrier P42 of the planetary gear mechanism P4 are The ring gear P33 of the planetary gear mechanism P3 and the ring gear P43 of the planetary gear mechanism P4 are connected by the connecting element R3. The ring gear P13 of the planetary gear mechanism P1 and the connecting element R3 (the ring gear P33 of the planetary gear mechanism P3 and the ring gear P43 of the planetary gear mechanism P4) are connected by the clutch C1, and the connecting element and the carrier P12 of the planetary gear mechanism P1. R3 (the ring gear P33 of the planetary gear mechanism P3 and the ring gear P43 of the planetary gear mechanism P4) are connected by the clutch C2, and the carrier P22 of the planetary gear mechanism P2 and the sun gear P31 of the planetary gear mechanism P1 are connected by the clutch C3. The sun gear P21 of the planetary gear mechanism P2 and the sun gear P31 of the planetary gear mechanism P3 are connected by a clutch C4. Further, the ring gear P13 of the planetary gear mechanism P1 is connected to the case 2 of the automatic transmission device 1 by the brake B1, and the sun gear P21 of the planetary gear mechanism P2 is connected to the case 2 of the automatic transmission device 1 by the brake B2. Has been. The carrier P22 of the planetary gear mechanism P2 is connected to the input shaft 3, and the carrier P12 of the planetary gear mechanism P1 is connected to the output shaft 4. Here, the four clutches C1, C2, C3, and C4 and the two brakes B1 and B2 are configured as hydraulically driven friction clutches and friction brakes that are engaged by pressing the friction plate with a piston in the embodiment. Has been.

  As described above, in the automatic transmission device 1 according to the embodiment, all of the four planetary gear mechanisms P1, P2, P3, and P4 are configured as single-pinion type planetary gear mechanisms. Since the double pinion type planetary gear mechanism has two rows of pinion gears in the radial direction, the pinion gears mesh with each other, resulting in an increase in gear meshing loss and transmission of power compared to the single pinion type planetary gear mechanism. Efficiency is reduced. Further, since the double pinion type planetary gear mechanism has two rows of pinion gears in the radial direction, the number of parts is increased and the assembling property and the economical efficiency are also reduced as compared with the single pinion type planetary gear mechanism. Since the four planetary gear mechanisms P1, P2, P3, and P4 of the automatic transmission device 1 of the embodiment are all configured as single pinion type planetary gear mechanisms, the four planetary gear mechanisms S1, S2, S3, Compared with the conventional automatic transmission device 901 in which three of S4 are configured as single-pinion type planetary gear mechanisms and one is configured as a double-pinion type planetary gear mechanism, the power transmission efficiency is higher. It is possible to improve the assembling property and the economical efficiency.

  The automatic transmission device 1 according to the embodiment thus configured advances from the first forward speed by a combination of engagement and release of the four clutches C1, C2, C3, and C4 and engagement and release of the two brakes B1 and B2. The 10th gear and the reverse gear can be switched. FIG. 2 shows an operation table of the automatic transmission device 1, and FIG. 3 shows a speed diagram of the planetary gear mechanisms P1, P2, P3, and P4 of the automatic transmission device 1. FIG. 3 shows, in order from the left, the speed diagram of the planetary gear mechanism P1, the speed diagram of the planetary gear mechanism P2, the speed diagram of the planetary gear mechanism P3, and the speed diagram of the planetary gear mechanism P4. The diagram is also arranged from the left in the order of sun gear, carrier, and ring gear. In FIG. 3, “1st” indicates the first forward speed, “2nd” indicates the second forward speed, “3rd” indicates the third forward speed, and “4th” to “10th” indicates the fourth forward speed. The 10th forward speed is shown from the stage, and “Rev” shows the reverse stage. “Λ1” to “λ4” indicate the gear ratios of the planetary gear mechanisms P1, P2, P3, and P4, and “B1” and “B2” indicate the brakes B1 and B2. “Input” indicates the connection position of the input shaft 3, and “Output” indicates the connection position of the output shaft 4.

  In the automatic transmission device 1 of the embodiment, as shown in FIG. 2, the forward 10th speed and the reverse speed are formed as follows from the first forward speed. The gear ratio (the number of revolutions of the input shaft 3 / the number of revolutions of the output shaft 4) is 0.40, 0.50, as the gear ratios λ1, λ2, λ3, and λ4 of the planetary gear mechanisms P1, P2, P3, and P4. The case where 0.45 and 0.30 were used was shown.

(1) The first forward speed can be established by engaging the clutch C3, the brake B1, and the brake B2 and releasing the clutch C1, the clutch C2, and the clutch C4, and the gear ratio is 4.667. Become.
(2) The second forward speed can be established by engaging the clutch C2, the clutch C3, and the brake B1 and releasing the clutch C1, the clutch C4, and the brake B2, and has a gear ratio of 2.859. Become.
(3) The third forward speed can be established by engaging the clutch C2, the clutch C4, and the brake B1, and releasing the clutch C1, the clutch C3, and the brake B2, and the gear ratio is 2.004. Become.
(4) The fourth forward speed can be formed by engaging the clutch C1, the clutch C4, and the brake B1, and releasing the clutch C2, the clutch C3, and the brake B2, and the gear ratio is 1.406. Become.

(5) The fifth forward speed can be established by engaging the clutch C1, the clutch C2, and the clutch C4 and releasing the clutch C3, the brake B1, and the brake B2, and the gear ratio is 1.000. Become.
(6) The sixth forward speed can be formed by engaging the clutch C1, the clutch C4, and the brake B2, and releasing the clutch C2, the clutch C3, and the brake B1, and the gear ratio is 0.747. Become.
(7) The seventh forward speed can be established by engaging the clutch C1, the clutch C3, and the brake B2 and releasing the clutch C2, the clutch C4, and the brake B1, and the gear ratio is 0.691. Become.
(8) The eighth forward speed can be formed by engaging the clutch C1, the clutch C2, and the brake B2 and releasing the clutch C3, the clutch C4, and the brake B1, and the gear ratio is 0.667. Become.

(9) The ninth forward speed can be established by engaging the clutch C2, the clutch C3, and the brake B2 and releasing the clutch C1, the clutch C4, and the brake B1, and has a gear ratio of 0.580. Become.
(10) The tenth forward speed can be formed by engaging the clutch C2, the clutch C4, and the brake B2, and releasing the clutch C1, the clutch C3, and the brake B1, and the gear ratio is 0.460. Become.
(11) The reverse gear can be formed by engaging the clutch C4, the brake B1, and the brake B2 and releasing the clutch C1, the clutch C2, and the clutch C3, and the gear ratio is −4.667. .

  Thus, in the automatic transmission device 1 according to the embodiment, the four planetary gear mechanisms P1, P2, P3, P4, the four clutches C1, C2, C3, C4 and the two brakes B1, B2 move forward from the first forward speed. An automatic transmission apparatus capable of shifting at the 10th speed and the reverse speed can be provided. As a result, the automatic transmission device 1 according to the embodiment has the number of shift stages on the forward side compared to the conventional automatic transmission apparatus that can shift from the first forward speed to the seventh forward speed and the reverse speed. Can do a lot. In the automatic transmission device 1 according to the embodiment, the gear ratio width (gear ratio of the lowest speed (first forward speed) / gear ratio of the highest speed (10 forward speed)) is 4.667 / 0.460. = 10.146, the gear ratio width can be increased as compared with the conventional automatic transmission apparatus having a gear ratio width of 6.06. As a result, the automatic transmission device 1 according to the embodiment can improve the fuel consumption while achieving both the fuel consumption and the acceleration of the mounted vehicle as compared with the automatic transmission device 901 according to the conventional example. At the same time, smooth acceleration before and after shifting can be maintained.

  Further, in the automatic transmission device 1 of the embodiment, any of the first forward speed, the 10th forward speed, and the reverse speed is made up of four clutches C1, C2, C3, C4 and two brakes B1, B2. Any one of the first forward speed, the seventh forward speed, and the reverse speed is formed by engaging and releasing three of the six engaging elements. The stage can also reduce the number of engagement elements to be released as compared with the conventional automatic transmission device that engages two of the six engagement elements and releases the four engagement elements. . Even if the engagement elements such as clutches and brakes are released, drag loss due to slight contact occurs. Therefore, if there are many engagement elements that are released when the gear stage is formed, the transmission efficiency decreases due to drag loss. To do. Therefore, since the automatic transmission device 1 of the embodiment has fewer engaging elements to be released than the automatic transmission device 901 of the conventional example, compared to the automatic transmission device 901 of the conventional example, Power transmission efficiency can be increased.

  According to the automatic transmission device 1 of the embodiment described above, the planetary gear mechanisms P1, P2, P3, P0, the four clutches C1, C2, C3, C4, and the two brakes B1, B2 are provided, The sun gear P11 of the gear mechanism P1 and the sun gear P41 of the planetary gear mechanism P4 are connected by a connecting element R1, and the ring gear P23 of the planetary gear mechanism P2, the carrier P32 of the planetary gear mechanism P3, and the carrier P42 of the planetary gear mechanism P4 are connected. The ring gear P33 of the planetary gear mechanism P3 and the ring gear P43 of the planetary gear mechanism P4 are connected by the connecting element R3, the ring gear P13 of the planetary gear mechanism P1 and the connecting element R3 are connected by the clutch C1, and the planetary gear mechanism is connected. The carrier P12 of P1 and the coupling element R3 are connected by the clutch C2, and the carrier P2 of the planetary gear mechanism P2 is connected. And the sun gear P31 of the planetary gear mechanism P1 are connected by the clutch C3, the sun gear P21 of the planetary gear mechanism P2 and the sun gear P31 of the planetary gear mechanism P3 are connected by the clutch C4, and the ring gear P13 of the planetary gear mechanism P1 is connected to the case 2 by the brake B1. , The sun gear P21 of the planetary gear mechanism P2 is connected to the case 2 by the brake B2, the carrier P22 of the planetary gear mechanism P2 is connected to the input shaft 3, and the carrier P12 of the planetary gear mechanism P1 is connected to the output shaft 4. Thus, it is possible to configure an automatic transmission apparatus capable of shifting from the first forward speed to the tenth forward speed and the reverse speed.

  In the automatic transmission device 1 of the embodiment, all of the four planetary gear mechanisms P1, P2, P3, and P4 are configured as single-pinion type planetary gear mechanisms. As compared with the conventional automatic transmission device in which one is configured as a single pinion type planetary gear mechanism and one is configured as a double pinion type planetary gear mechanism, the power transmission efficiency can be increased. At the same time, the assembly and economical efficiency of the apparatus can be improved.

  Further, in the automatic transmission device 1 according to the embodiment, 0.40, 0.50, 0.45, and 0.30 are used as the gear ratios λ1, λ2, λ3, and λ4 of the planetary gear mechanisms P1, P2, P3, and P4. As a result, the gear ratio width becomes 10.146, so that the gear ratio width can be increased as compared with the conventional automatic transmission apparatus having the gear ratio width of 6.06. As a result, it is possible to improve the fuel efficiency of the vehicle on which the vehicle is mounted and to improve the feeling of acceleration / deceleration before and after the shift as compared with the conventional automatic transmission device.

  In addition, in the automatic transmission device 1 according to the embodiment, any of the shift speeds from the first forward speed to the tenth forward speed and the reverse speed includes four clutches C1, C2, C3, C4 and two brakes B1, B2. Any one of the first forward speed to the seventh forward speed and the reverse speed is formed by engaging and releasing the three engagement elements of the six engagement elements. The stage can also reduce the number of engagement elements to be released as compared with the conventional automatic transmission device that engages two of the six engagement elements and releases the four engagement elements. . As a result, power transmission efficiency can be increased as compared with the conventional automatic transmission device.

  In the automatic transmission device 1 of the embodiment, all of the four clutches C1, C2, C3, and C4 are configured as friction clutches, and all of the two brakes B1 and B3 are configured as friction brakes. These clutches and brakes may be constituted by dog clutches or dog brakes instead of friction clutches or friction brakes. FIG. 4 shows a modified automatic transmission device 1B with respect to the automatic transmission device 1 in which the brake B1 is configured as a dog brake. The operation table and speed diagram of the automatic transmission device 1B according to the modification are the same as those in FIGS. The dog brake is susceptible to shock when engaged, and synchronous control is required to synchronize the rotation. However, the brake B1 is continuously engaged from the first forward speed to the fourth forward speed, and from the fifth forward speed to the forward 10 speed. Since the release is continued up to the speed stage, the engagement and release are not repeated frequently, and the frequency of occurrence of the synchronous control is low. For this reason, even if the dog brake is employed, the deterioration of the shift feeling is suppressed.

  In the automatic transmission device 1 of the embodiment, 0.40, 0.50, 0.45, and 0.30 are used as the gear ratios λ1, λ2, λ3, and λ4 of the four planetary gear mechanisms P1, P2, P3, and P4. However, the gear ratios λ1, λ2, λ3, and λ4 are not limited to these values.

  In the automatic transmission device 1 of the embodiment, the four planetary gear mechanisms P1, P2, P3, and P4 are all configured as single-pinion type planetary gear mechanisms, but the four planetary gear mechanisms P1, P2, A part or all of P3 and P4 may be configured as a double pinion planetary gear mechanism.

  In the automatic transmission device 1 according to the embodiment, three engagement elements of six engagement elements including four clutches C1, C2, C3, and C4 and two brakes B1 and B2 are engaged and three By forming by releasing the engaging element, the automatic transmission device is configured to be capable of changing from the first forward speed to the tenth forward speed and the reverse speed. The automatic transmission device may be capable of 9-speed shifting excluding any one of these shift speeds or 8th speed shift or less shifting except for a plurality of shift speeds and a reverse speed.

  In the automatic transmission device 1 of the embodiment, the engine is mounted on a vehicle of a type (for example, a front engine rear drive type) in which the engine is placed vertically (in the front-rear direction of the vehicle). As shown in the automatic transmission 1C, an output gear 4b is provided instead of the output shaft 4, and the engine is mounted on a vehicle (for example, a front engine front drive type) in which the engine is placed horizontally (in the left-right direction of the vehicle). It is good also as a thing.

  Here, the correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problems will be described. In the embodiment, the input shaft (input shaft) 3 corresponds to “input member”, the output shaft 4 corresponds to “output member”, the planetary gear mechanism P1 corresponds to “planetary gear mechanism P1”, and the sun gear P11 Corresponding to “rotating element P11”, carrier P12 corresponds to “rotating element P12”, ring gear P13 corresponds to “rotating element P13”, planetary gear mechanism P2 corresponds to “planetary gear mechanism P2”, and sun gear P21. Corresponds to “rotating element P21”, carrier P22 corresponds to “rotating element P22”, ring gear P23 corresponds to “rotating element P23”, planetary gear mechanism P3 corresponds to “planetary gear mechanism P3”, and sun gear. P31 corresponds to “rotating element P31”, carrier P32 corresponds to “rotating element P32”, ring gear P33 corresponds to “rotating element P33”, and planetary gear mechanism P4 corresponds to “idling element”. It corresponds to the gear mechanism P4, the sun gear P41 corresponds to the “rotating element P41”, the carrier P42 corresponds to the “rotating element P42”, the ring gear P43 corresponds to the “rotating element P43”, and the connecting element R1 is “connected”. Element R1 ", connection element R2 corresponds to" connection element R2 ", connection element R3 corresponds to" connection element R3 ", clutch C1 corresponds to" clutch C1 ", and clutch C2 corresponds to" clutch C2 ". ", The clutch C3 corresponds to" clutch C3 ", the clutch C4 corresponds to" clutch C4 ", the brake B1 corresponds to" brake B1 ", and the brake B2 corresponds to" brake B2 ". The correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problem is the same as that of the embodiment described in the column of means for solving the problem. It is an example for specifically explaining the best mode for doing so, and does not limit the elements of the invention described in the column of means for solving the problem. That is, the interpretation of the invention described in the column of means for solving the problems should be made based on the description of the column, and the examples are those of the invention described in the column of means for solving the problems. It's just a concrete example

  The best mode for carrying out the present invention has been described with reference to the embodiments. However, the present invention is not limited to these embodiments, and various modifications can be made without departing from the gist of the present invention. Of course, it can be implemented in the form.

  The present invention is applicable to the manufacturing industry of automatic transmission devices.

  1, 1B automatic transmission device, 2 case (automatic transmission device case), 3 input shaft, 4 output shaft, 4b output gear, P1, P2, P3, P4 planetary gear mechanism, P11, P21, P31, P41 sun gear, P12, P22, P32, P42 Carrier, P13, P23, P33, P43 Ring gear, P14, P24, P34, P44 Pinion gear, R1, R2, R3 connecting element, C1, C2, C3, C4 clutch, B1, B2 brake.

Claims (4)

An automatic transmission device that shifts the power input to the input member and outputs it to the output member,
A planetary gear mechanism P1 having a rotation element P11, a rotation element P12, and a rotation element P13 in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
A planetary gear mechanism P2 having a rotation element P21, a rotation element P22, and a rotation element P23 in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
A planetary gear mechanism P3 having a rotating element P31, a rotating element P32, and a rotating element P33 in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
A planetary gear mechanism P4 having a rotation element P41, a rotation element P42, and a rotation element P43 in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
A connecting element R1 that connects the rotating element P11 and the rotating element P41;
A connecting element R2 that connects the rotating element P23, the rotating element P32, and the rotating element P42;
A connecting element R3 that connects the rotating element P33 and the rotating element P43;
A clutch C1 that engages the rotation element P13 and the coupling element R3 and releases the engagement;
A clutch C2 that engages and disengages the rotating element P12 and the connecting element R3;
A clutch C3 for engaging and releasing the rotation element P22 and the rotation element P31;
A clutch C4 for engaging and releasing the rotation element P21 and the rotation element P31;
A brake B1 that engages the rotating element P13 in a fixed manner with an automatic transmission device case and releases the engagement;
A brake B2 for engaging the rotating element P21 with the automatic transmission device case in a fixable manner and releasing the engagement;
With
Connecting the input member to the rotating element P22;
The output member is connected to the rotating element P12.
An automatic transmission device characterized by that. The automatic transmission device according to claim 1,
The first forward speed is formed by engaging the clutch C3, the brake B1, and the brake B2, and releasing the clutch C1, the clutch C2, and the clutch C4.
The second forward speed is formed by engaging the clutch C2, the clutch C3, and the brake B1, and releasing the clutch C1, the clutch C4, and the brake B2.
The third forward speed is formed by engaging the clutch C2, the clutch C4, and the brake B1, and releasing the clutch C1, the clutch C3, and the brake B2.
The fourth forward speed is formed by engaging the clutch C1, the clutch C4, and the brake B1, and releasing the clutch C2, the clutch C3, and the brake B2.
The fifth forward speed is formed by engaging the clutch C1, the clutch C2, and the clutch C4 and releasing the clutch C3, the brake B1, and the brake B2.
The sixth forward speed is formed by engaging the clutch C1, the clutch C4, and the brake B2 and releasing the clutch C2, the clutch C3, and the brake B1,
The seventh forward speed is formed by engaging the clutch C1, the clutch C3, and the brake B2 and releasing the clutch C2, the clutch C4, and the brake B1,
The eighth forward speed is formed by engaging the clutch C1, the clutch C2, and the brake B2, and releasing the clutch C3, the clutch C4, and the brake B1,
The ninth forward speed is formed by engaging the clutch C2, the clutch C3, and the brake B2, and releasing the clutch C1, the clutch C4, and the brake B1,
The 10th forward speed is formed by engaging the clutch C2, the clutch C4, and the brake B2, and releasing the clutch C1, the clutch C3, and the brake B1,
The reverse gear is formed by engaging the clutch C4, the brake B1, and the brake B2 and releasing the clutch C1, the clutch C2, and the clutch C3.
An automatic transmission device characterized by that. The automatic transmission device according to claim 1 or 2,
The planetary gear mechanism P1, the planetary gear mechanism P2, the planetary gear mechanism P3, and the planetary gear mechanism P4 are all configured as a single pinion type planetary gear mechanism having a sun gear, a ring gear, and a carrier as the three rotating elements. Being
The rotating element P11, the rotating element P21, the rotating element P31, and the rotating element P41 are all sun gears,
The rotating element P12, the rotating element P22, the rotating element P32, and the rotating element P42 are all carriers.
The rotating element P13, the rotating element P23, the rotating element P33, and the rotating element P43 are all ring gears.
An automatic transmission device characterized by that. An automatic transmission device according to any one of claims 1 to 3,
The brake B1 is configured as a dog brake,
An automatic transmission device characterized by that.

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