JP6184364B2 - Multi-speed transmission - Google Patents

Description

  The present invention relates to a multi-stage transmission that shifts power transmitted from a prime mover of a vehicle to an input member and transmits the power to an output member.

  Conventionally, this type of multi-speed transmission includes four single pinion planetary gears, four clutches, and two brakes, and includes forward and reverse speeds from the first speed to the tenth speed. What is provided is known (see, for example, Patent Document 1). In such a multi-stage transmission, as the spread (gear ratio width = gear ratio of the lowest speed stage / gear ratio of the highest speed stage) is increased, the power transmission efficiency, that is, the fuel consumption of the vehicle on which the multi-stage transmission is mounted, etc. In addition, drivability, that is, acceleration performance of the vehicle can be further improved.

US Patent Application Publication No. 2012/0231917

  However, in the multi-stage transmission described in Patent Document 1, when the gear ratio of the lowest gear is 4.600 and the gear ratio of the highest gear is 0.638, the spread is 7.21 and the lowest When the gear ratio of the gear stage is 4.850 and the gear ratio of the highest gear stage is 0.616, the spread is 7.89. There is still room for improvement in terms of improving fuel economy and drivability. Further, in the multi-stage transmission described in Patent Document 1, the first planetary gear (reference numeral 14) having a particularly large diameter is formed when the forward second speed to the sixth speed and the forward eighth speed to the tenth speed are formed. ) Always rotates at a high rotation speed, the inertia during the rotation of the ring gear increases. For this reason, it takes time to engage the brake or clutch (shifting time becomes long), a shock may occur at the time of shifting involving the engagement of the brake, etc., and the durability of the friction material of the brake or clutch May deteriorate.

  Therefore, the main object of the present invention is to further improve the fuel consumption, drivability, speed change performance, and durability of the engagement element of a vehicle in which a multi-stage transmission is mounted.

  The multi-stage transmission according to the present invention adopts the following means in order to achieve the main object.

The multi-stage transmission according to the present invention is
In a multi-stage transmission that shifts the power transmitted to the input member and transmits it to the output member,
A first planetary gear having a first rotating element, a second rotating element, and a third rotating element arranged in order at intervals corresponding to the gear ratio on the velocity diagram;
A second planetary gear having a fourth rotating element, a fifth rotating element, and a sixth rotating element arranged in order at intervals corresponding to the gear ratio on the velocity diagram;
A third planetary gear having a seventh rotating element, an eighth rotating element, and a ninth rotating element arranged in order at intervals corresponding to the gear ratio on the velocity diagram;
A fourth planetary gear having a tenth rotating element, an eleventh rotating element, and a twelfth rotating element arranged in order at intervals corresponding to the gear ratio on the velocity diagram;
The first, second, third and fourth rotating elements of the first, second, third and fourth planetary gears are connected to other rotating elements or stationary members, respectively, and the connection between them is released. And fifth and sixth engaging elements,
The fifth rotating element of the second planetary gear is always connected to the input member;
The eighth rotating element of the third planetary gear is always connected to the output member;
The first rotating element of the first planetary gear and the seventh rotating element of the third planetary gear are always connected,
The second rotating element of the first planetary gear and the fifth rotating element of the second planetary gear are always connected,
The third rotating element of the first planetary gear and the eleventh rotating element of the fourth planetary gear are always connected,
The fourth rotating element of the second planetary gear and the tenth rotating element of the fourth planetary gear are always connected,
The first engagement element includes the always connected third rotation element of the first planetary gear and the eleventh rotation element of the fourth planetary gear, and the eighth rotation element of the third planetary gear. Connect with each other, disconnect both,
The second engaging element connects the sixth rotating element of the second planetary gear and the ninth rotating element of the third planetary gear to each other, and releases the connection between them.
The third engaging element includes the first rotating element of the first planetary gear, the seventh rotating element of the third planetary gear, and the sixth rotating element of the second planetary gear that are always connected. Connect with each other, disconnect both,
The fourth engaging element connects the second rotating element of the first planetary gear, the fifth rotating element of the second planetary gear, and the twelfth rotating element of the fourth planetary gear, which are always connected to each other. Connect and disconnect both,
The fifth engaging element connects the fourth rotating element of the second planetary gear and the tenth rotating element of the fourth planetary gear, which are always connected, to a stationary member and fixes them in a non-rotatable manner. Disconnect
The sixth engaging element connects the ninth rotating element of the third planetary gear to a stationary member and fixes it to be non-rotatable, and releases the connection between them.
Advancement from the first speed to the tenth speed by selectively engaging any three of the first, second, third, fourth, fifth and sixth engagement elements A step and a reverse step are formed.

  In the multi-stage transmission configured as described above, since the spread can be increased, the vehicle in which the multi-stage transmission is mounted by increasing the low-speed gear ratio and decreasing the high-speed gear ratio. As a result, the drivability, that is, the acceleration performance of the vehicle and the like can be further improved. Further, in this multi-stage transmission, when planetary gears including ring gears are used as the first, second, third and fourth planetary gears, the forward gear and the reverse gear from the first gear to the tenth gear are used. It is possible to prevent an increase in inertia during rotation of the ring gear by preventing the ring gear having a particularly large diameter from rotating at a high rotational speed during formation. As a result, the time required for engaging the engaging element is shortened, the occurrence of shock at the time of shifting accompanied by the engagement of the engaging element is suppressed, and the durability of the friction material of the engaging element is improved. Can be secured. As a result, in the multi-stage transmission according to the present invention, it becomes possible to further improve the fuel consumption, drivability, speed change performance, and durability of the engagement element of the vehicle in which the multi-stage transmission is mounted.

1 is a schematic configuration diagram of a power transmission device including a multi-stage transmission according to an embodiment of the present invention. FIG. 2 is a velocity diagram showing a ratio of a rotational speed of each rotary element to an input rotational speed in the multi-stage transmission of FIG. FIG. 2 is an operation table showing the relationship between each shift stage and the operation states of clutches and brakes in the multi-stage transmission of FIG. 1.

  Next, the form for implementing this invention is demonstrated, referring drawings.

  FIG. 1 is a schematic configuration diagram of a power transmission device 10 including an automatic transmission 20 as a multi-stage transmission according to an embodiment of the present invention. A power transmission device 10 shown in these drawings is connected to a crankshaft of an engine (internal combustion engine) (not shown) as a drive source mounted horizontally in a front portion of a front-wheel drive vehicle and power (torque) from the engine. Can be transmitted to left and right front wheels (drive wheels) (not shown). As shown in the figure, the power transmission device 10 shifts the power transmitted from the engine to the input shaft 20i and transmits it to a counter drive gear 41 as an output member, in addition to a transmission case (stationary member). 11, a starting device (fluid transmission device) 12, an oil pump 17, and the like.

  The starting device 12 includes an input-side pump impeller 14p connected to the drive source as described above, an output-side turbine runner 14t connected to the input shaft (input member) 20i of the automatic transmission 20, a pump impeller 14p, A stator 14s that is disposed inside the turbine runner 14t and rectifies the flow of hydraulic oil from the turbine runner 14t to the pump impeller 14p. A one-way clutch that is supported by a stator shaft (not shown) and restricts the rotational direction of the stator 14s in one direction. Including a torque converter having 14o and the like. Further, the starting device 12 connects the front cover connected to the crankshaft of the engine and the like and the input shaft 20i of the automatic transmission 20 to each other, and releases the connection between the front cover and the automatic transmission. And a damper mechanism 16 that damps vibration between the input shaft 20 i of the machine 20. The starting device 12 may include a fluid coupling that does not have the stator 14s.

  The oil pump 17 includes a pump assembly including a pump body and a pump cover, an external gear (inner rotor) connected to the pump impeller 14p of the starting device 12, an internal gear (outer rotor) meshed with the external gear, and the like. It is comprised as a gear pump having. The oil pump 17 is driven by power from the engine, sucks hydraulic oil (ATF) stored in an oil pan (not shown), and pumps it to a hydraulic control device (not shown).

  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 drive gear 41 as an output member, and an automatic transmission 20 (input shaft 20i) a single pinion type first planetary gear 21, a single pinion type second planetary gear 22, a single pinion type third planetary gear 23, and a single pinion type fourth planetary gear 20i). 24. Further, the automatic transmission 20 includes a clutch C1 as a first engagement element for changing a power transmission path from the input shaft 20i to the counter drive gear 41 as an output member, a clutch C2 as a second engagement element, A clutch C3 as a third engagement element, a clutch C4 as a fourth engagement element, a brake B1 as a fifth engagement element, and a brake B2 as a sixth engagement element are included. The power (torque) transmitted from the automatic transmission 20 to the counter drive gear 41 is transmitted to the counter driven gear 42 via the counter drive gear 41 and the counter driven gear 42 meshing with the counter drive gear 41 and the counter shaft 43. Via a drive shaft 51, a gear train 40 having a drive pinion gear (final drive gear) 44, a differential ring gear (final driven gear) 45 meshing with the drive pinion gear 44, a differential gear 50 connected to the differential ring gear 45, and a drive shaft 51. Is transmitted to the left and right front wheels.

  In the present embodiment, the first planetary gear 21, the second planetary gear 22, the third planetary gear 23, and the fourth planetary gear 24 are connected to the second planetary gear 22, from the starting device 12, that is, from the engine side (the right side in FIG. 1). The third planetary gear 23, the first planetary gear 21, and the fourth planetary gear 24 are arranged in the transmission case 11 so as to be arranged in this order. The clutch C1 is disposed between, for example, the first planetary gear 21 and the third planetary gear 23, and the clutches C2 and C3 are disposed, for example, between the second planetary gear 22 and the third planetary gear 23. The clutch C4 is disposed, for example, between the first planetary gear 21 and the fourth planetary gear 24, the brake B1 is disposed, for example, on the opposite side of the starting device 12 with respect to the fourth planetary gear 24, and the brake B2 is For example, it is arranged outside the third planetary gear 23 or the clutches C2 and C3.

  The first planetary gear 21 includes a first sun gear 21s that is an external gear, a first ring gear 21r that is an internal gear disposed concentrically with the first sun gear 21s, and a first sun gear 21s and a first ring gear 21r, respectively. And a first carrier 21c that holds the plurality of first pinion gears 21p so as to freely rotate (rotate) and revolve. In the present embodiment, the gear ratio λ1 of the first planetary gear 21 (the number of teeth of the first sun gear 21s / the number of teeth of the first ring gear 21r) is set to λ1 = 0.370, for example.

  The second planetary gear 22 includes a second sun gear 22s that is an external gear, a second ring gear 22r that is an internal gear disposed concentrically with the second sun gear 22s, and a second sun gear 22s and a second ring gear 22r, respectively. And a second carrier 22c that holds the plurality of second pinion gears 22p so that they can rotate (rotate) and revolve freely. In the present embodiment, the gear ratio λ2 of the second planetary gear 22 (the number of teeth of the second sun gear 22s / the number of teeth of the second ring gear 22r) is set to λ2 = 0.500, for example.

  The third planetary gear 23 includes a third sun gear 23s that is an external gear, a third ring gear 23r that is an internal gear disposed concentrically with the third sun gear 23s, and a third sun gear 23s and a third ring gear 23r, respectively. And a third carrier 23c that holds the plurality of third pinion gears 23p so that they can rotate (rotate) and revolve freely. In the present embodiment, the gear ratio λ3 of the third planetary gear 23 (the number of teeth of the third sun gear 23s / the number of teeth of the third ring gear 23r) is set to λ3 = 0.250, for example.

  The fourth planetary gear 24 includes a fourth sun gear 24s that is an external gear, a fourth ring gear 24r that is an internal gear disposed concentrically with the fourth sun gear 24s, and a fourth sun gear 24s and a fourth ring gear 24r, respectively. And a fourth carrier 24c that holds the plurality of fourth pinion gears 24p so as to freely rotate (rotate) and revolve. In the present embodiment, the gear ratio λ4 of the fourth planetary gear 24 (the number of teeth of the fourth sun gear 24s / the number of teeth of the fourth ring gear 24r) is set to λ4 = 0.600, for example.

  As shown in FIG. 1, the second carrier 22c of the second planetary gear 22 is always connected to the input shaft 20i, and is connected to the first carrier 21c of the first planetary gear 21 via a connecting member. The input shaft 20i, the first carrier 21c, and the second carrier 22c always rotate or stop integrally (and coaxially). The third carrier 23c of the third planetary gear 23 is always connected to a counter drive gear 41 as an output member. Further, the first sun gear 21s of the first planetary gear 21 and the third sun gear 23s of the third planetary gear 23 are always connected via a connecting member, and always rotate or stop integrally (and coaxially). The first ring gear 21r of the first planetary gear 21 and the fourth carrier 24c of the fourth planetary gear 24 are always connected via a connecting member, and always rotate or stop integrally (and coaxially). Further, the second sun gear 22s of the second planetary gear 22 and the fourth sun gear 24s of the fourth planetary gear 24 are always connected via a connecting member, and always rotate or stop integrally (and coaxially).

  The clutch C1 connects the first ring gear 21r of the first planetary gear 21 and the fourth carrier 24c of the fourth planetary gear 24, and the third carrier 23c of the third planetary gear 23, which are always coupled, Disconnect the connection. The clutch C2 connects and disconnects the second ring gear 22r of the second planetary gear 22 and the third ring gear 23r of the third planetary gear 23 from each other. The clutch C3 connects the first sun gear 21s of the first planetary gear 21 and the third sun gear 23s of the third planetary gear 23 and the second ring gear 22r of the second planetary gear 22 that are always connected to each other. Disconnect the connection. The clutch C4 connects the first carrier 21c of the first planetary gear 21 and the second carrier 22c of the second planetary gear 22 that are always connected to each other and the fourth ring gear 24r of the fourth planetary gear 24. Disconnect the connection.

  The brake B1 fixes (connects) the second sun gear 22s of the second planetary gear 22 and the fourth sun gear 24s of the fourth planetary gear 24 that are always connected to the transmission case 11 as a stationary member in a non-rotatable manner. The second sun gear 22 s and the fourth sun gear 24 s are freely released with respect to the transmission case 11. The brake B2 fixes (connects) the third ring gear 23r of the third planetary gear 23 to the transmission case 11 as a stationary member in a non-rotatable manner and releases the third ring gear 23r so as to be rotatable with respect to the transmission case 11. To do.

  In this embodiment, as the clutches C1 to C4, a piston, a plurality of friction engagement plates (for example, a friction plate formed by sticking a friction material on both surfaces of an annular member, and an annular member formed smoothly on both surfaces) A multi-plate friction type hydraulic clutch (friction engagement element) having a hydraulic servo composed of a separator plate), an engagement oil chamber to which hydraulic oil is supplied, a centrifugal oil pressure cancellation chamber, and the like are employed. Further, 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, and the like. Is adopted. The clutches C1 to C4 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 of the input shaft 20i (input rotational speed) in the automatic transmission 20 (however, the input shaft 20i, that is, the second carrier 22c and the first carrier 22c). The rotation speed of the carrier 21c is set to a value of 1. The same applies hereinafter. 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 C4 and the brakes B1 and B2.

  As shown in FIG. 2, the three rotating elements constituting the single 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 carrier 21c, and the first ring gear 21r are arranged in this order from the left side in the figure at an interval corresponding to the gear ratio λ1 on the figure (the leftmost speed diagram in FIG. 2). In accordance with the order of arrangement in the speed diagram, in the present invention, the first sun gear 21s is the first rotating element of the automatic transmission 20, the first carrier 21c is the second rotating element of the automatic transmission 20, and the first The ring gear 21r is a 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.

  Further, 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 velocity diagrams of the second planetary gear 22 (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 left side in the drawing with an interval corresponding to the gear ratio λ2 on the second speed diagram from the left). According to the arrangement order in the speed diagram, in the present invention, 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, and the second The ring gear 22r is the 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.

  Further, the three rotating elements constituting the single pinion type third planetary gear 23, that is, the third sun gear 23s, the third ring gear 23r, and the third carrier 23c are speed diagrams of the third planetary gear 23 (in FIG. 2). The second sun gear 23s, the third carrier 23c, and the third ring gear 23r are arranged in this order from the left side in the drawing at intervals corresponding to the gear ratio λ3 on the second speed diagram from the right). According to the arrangement order in the speed diagram, in the present invention, the third sun gear 23s is the seventh rotating element of the automatic transmission 20, the third carrier 23c is the eighth rotating element of the automatic transmission 20, and the third The ring gear 23r is the ninth rotating element of the automatic transmission 20. Therefore, the third planetary gear 23 has the seventh rotation element, the eighth rotation element, and the ninth rotation element of the automatic transmission 20 that are arranged in order at intervals corresponding to the gear ratio λ3 on the velocity diagram.

  Further, the three rotating elements constituting the single pinion type fourth planetary gear 24, that is, the fourth sun gear 24s, the fourth ring gear 24r, and the fourth carrier 24c are speed diagrams of the fourth planetary gear 24 (in FIG. 2). On the rightmost speed diagram), the fourth sun gear 24s, the fourth carrier 24c, and the fourth ring gear 24r are arranged in this order from the left side in the figure at intervals corresponding to the gear ratio λ4. According to the arrangement order in the speed diagram, in the present invention, the fourth sun gear 24s is the tenth rotating element of the automatic transmission 20, the fourth carrier 24c is the eleventh rotating element of the automatic transmission 20, and the fourth The ring gear 24r is a twelfth rotating element of the automatic transmission 20. Accordingly, the fourth planetary gear 24 has the tenth rotation element, the eleventh rotation element, and the twelfth rotation element of the automatic transmission 20 that are arranged in order at intervals corresponding to the gear ratio λ4 on the velocity diagram.

  In the automatic transmission 20, the clutches C <b> 1 to C <b> 4 and the brakes B <b> 1 and B <b> 2 are engaged or released as shown in FIG. 3 to change the connection relationship of the first to twelfth rotating elements described above. There are 10 power transmission paths in the forward rotation direction and one reverse rotation direction between 20i and the counter drive gear 41 as the output member, 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 clutches C3 and C4 and the brake B2 and releasing the remaining clutches C1 and C2 and the brake B1. That is, when the first forward speed is formed, the first sun gear 21s of the first planetary gear 21 and the third sun gear 23s of the third planetary gear 23 and the second ring gear 22r of the second planetary gear 22 are mutually connected by the clutch C3. In addition, the first carrier 21c of the first planetary gear 21 and the second carrier 22c of the second planetary gear 22 and the fourth ring gear 24r of the fourth planetary gear 24 are connected to each other by the clutch C4, and the brake B2 Thus, the third ring gear 23r of the third planetary gear 23 is fixed to the transmission case 11 so as not to rotate. In this embodiment (when the gear ratios of the first to fourth planetary gears 21 to 24 are λ1 = 0.370, λ2 = 0.500, λ3 = 0.250, λ4 = 0.600, the same applies hereinafter) The gear ratio (rotational speed of the input shaft 20i / rotational speed of the counter drive gear 41) γ1 at the first forward speed is γ1 = 5.000.

  The second forward speed is formed by engaging the clutch C3 and the brakes B1 and B2 and disengaging the remaining clutches C1, C2, and C4. That is, when the second forward speed is established, the first sun gear 21s of the first planetary gear 21 and the third sun gear 23s of the third planetary gear 23 and the second ring gear 22r of the second planetary gear 22 are mutually connected by the clutch C3. Furthermore, the second sun gear 22s of the second planetary gear 22 and the fourth sun gear 24s of the fourth planetary gear 24 are non-rotatably fixed to the transmission case 11 by the brake B1, and the third planetary gear by the brake B2. The third ring gear 23r of the gear 23 is fixed to the transmission case 11 so as not to rotate. In the present embodiment, the gear ratio γ2 at the second forward speed is γ2 = 3.333. The step ratio between the first forward speed and the second forward speed is γ1 / γ2 = 1.500.

  The third forward speed is formed by engaging the clutch C4 and the brakes B1 and B2 and releasing the remaining clutches C1, C2, and C3. That is, when the third forward speed is established, the first carrier 21c of the first planetary gear 21 and the second carrier 22c of the second planetary gear 22 and the fourth ring gear 24r of the fourth planetary gear 24 are mutually connected by the clutch C4. Furthermore, the second sun gear 22s of the second planetary gear 22 and the fourth sun gear 24s of the fourth planetary gear 24 are non-rotatably fixed to the transmission case 11 by the brake B1, and the third planetary gear by the brake B2. The third ring gear 23r of the gear 23 is fixed to the transmission case 11 so as not to rotate. In the present embodiment, the gear ratio γ3 at the third forward speed is γ3 = 2.483. The step ratio between the second forward speed and the third forward speed is γ2 / γ3 = 1.342.

  The fourth forward speed is formed by engaging the clutch C1 and the brakes B1 and B2 and releasing the remaining clutches C2, C3, and C4. That is, when the fourth forward speed is established, the first ring gear 21r of the first planetary gear 21 and the fourth carrier 24c of the fourth planetary gear 24 and the third carrier 23c of the third planetary gear 23 are mutually connected by the clutch C1. Furthermore, the second sun gear 22s of the second planetary gear 22 and the fourth sun gear 24s of the fourth planetary gear 24 are non-rotatably fixed to the transmission case 11 by the brake B1, and the third planetary gear by the brake B2. The third ring gear 23r of the gear 23 is fixed to the transmission case 11 so as not to rotate. In the present embodiment, the gear ratio γ4 at the fourth forward speed is γ4 = 2.080. The step ratio between the third forward speed and the fourth forward speed is γ3 / γ4 = 1.194.

  The fifth forward speed is formed by engaging the clutches C1 and C4 and the brake B1 and releasing the remaining clutches C2 and C3 and the brake B2. That is, when the fifth forward speed is established, the clutch C1 causes the first ring gear 21r of the first planetary gear 21, the fourth carrier 24c of the fourth planetary gear 24, and the third carrier 23c of the third planetary gear 23 to each other. In addition, the first carrier 21c of the first planetary gear 21 and the second carrier 22c of the second planetary gear 22 and the fourth ring gear 24r of the fourth planetary gear 24 are connected to each other by the clutch C4, and the brake B1. Thus, the second sun gear 22 s of the second planetary gear 22 and the fourth sun gear 24 s of the fourth planetary gear 24 are fixed to the transmission case 11 so as not to rotate. In the present embodiment, the gear ratio γ5 at the fifth forward speed is γ5 = 1.600. The step ratio between the fourth forward speed and the fifth forward speed is γ4 / γ5 = 1.300.

  The sixth forward speed is formed by engaging the clutches C1, C3 and the brake B1, and releasing the remaining clutches C2, C4 and the brake B2. That is, when the sixth forward speed is established, the first ring gear 21r of the first planetary gear 21 and the fourth carrier 24c of the fourth planetary gear 24 and the third carrier 23c of the third planetary gear 23 are mutually connected by the clutch C1. In addition, the first sun gear 21s of the first planetary gear 21 and the third sun gear 23s of the third planetary gear 23 and the second ring gear 22r of the second planetary gear 22 are connected to each other by the clutch C3, and the brake B1. Thus, the second sun gear 22 s of the second planetary gear 22 and the fourth sun gear 24 s of the fourth planetary gear 24 are fixed to the transmission case 11 so as not to rotate. In the present embodiment, the gear ratio γ6 at the sixth forward speed is γ6 = 1.227. The step ratio between the fifth forward speed and the sixth forward speed is γ5 / γ6 = 1.304.

  The seventh forward speed is formed by engaging the clutches C1, C2, and C3 and disengaging the remaining clutch C4 and brakes B1 and B2. That is, when the seventh forward speed is established, the first ring gear 21r of the first planetary gear 21 and the fourth carrier 24c of the fourth planetary gear 24 and the third carrier 23c of the third planetary gear 23 are mutually connected by the clutch C1. The second ring gear 22r of the second planetary gear 22 and the third ring gear 23r of the third planetary gear 23 are connected to each other by the clutch C2, and further, the first sun gear 21s and the first sun gear 21s of the first planetary gear 21 are connected by the clutch C3. The third sun gear 23s of the three planetary gear 23 and the second ring gear 22r of the second planetary gear 22 are connected to each other. In the present embodiment, the gear ratio γ7 at the seventh forward speed is γ7 = 1.000. The step ratio between the sixth forward speed and the seventh forward speed is γ6 / γ7 = 1.227.

  The eighth forward speed is formed by engaging the clutches C1 and C2 and the brake B1, and releasing the remaining clutches C3 and C4 and the brake B2. That is, when forming the eighth forward speed, the clutch C1 causes the first ring gear 21r of the first planetary gear 21 and the fourth carrier 24c of the fourth planetary gear 24 and the third carrier 23c of the third planetary gear 23 to communicate with each other. The second ring gear 22r of the second planetary gear 22 and the third ring gear 23r of the third planetary gear 23 are connected to each other by the clutch C2, and the second sun gear 22s of the second planetary gear 22 is further connected to the brake B1. The fourth sun gear 24 s of the fourth planetary gear 24 is fixed to the transmission case 11 so as not to rotate. In the present embodiment, the gear ratio γ8 at the eighth forward speed is γ8 = 0.794. The step ratio between the seventh forward speed and the eighth forward speed is γ7 / γ8 = 1.260.

  The ninth forward speed is established by engaging the clutches C2 and C3 and the brake B1, and releasing the remaining clutches C1 and C4 and the brake B2. That is, when the ninth forward speed is established, the second ring gear 22r of the second planetary gear 22 and the third ring gear 23r of the third planetary gear 23 are connected to each other by the clutch C2, and the first planetary gear by the clutch C3. The first sun gear 21s of the gear 21, the third sun gear 23s of the third planetary gear 23, and the second ring gear 22r of the second planetary gear 22 are connected to each other, and further, the second sun gear 22s of the second planetary gear 22 by the brake B1. The fourth sun gear 24 s of the fourth planetary gear 24 is fixed to the transmission case 11 so as not to rotate. In the present embodiment, the gear ratio γ9 at the ninth forward speed is γ9 = 0.667. The step ratio between the eighth forward speed and the ninth forward speed is γ8 / γ9 = 1.191.

  The tenth forward speed is formed by engaging the clutches C2 and C4 and the brake B1 and releasing the remaining clutches C1 and C3 and the brake B2. That is, when the forward tenth speed is established, the second ring gear 22r of the second planetary gear 22 and the third ring gear 23r of the third planetary gear 23 are connected to each other by the clutch C2, and the first planetary gear by the clutch C4. The first carrier 21c of the gear 21 and the second carrier 22c of the second planetary gear 22 and the fourth ring gear 24r of the fourth planetary gear 24 are connected to each other, and further, the second sun gear 22s of the second planetary gear 22 by the brake B1. The fourth sun gear 24 s of the fourth planetary gear 24 is fixed to the transmission case 11 so as not to rotate. In the present embodiment, the gear ratio γ10 at the tenth forward speed is γ10 = 0.624. The step ratio between the ninth forward speed and the tenth forward speed is γ9 / γ10 = 1.068. The spread in the automatic transmission 20 (gear ratio width = gear ratio γ1 at the first forward speed, which is the lowest speed) / gear ratio γ10 at the tenth speed, which is the highest speed, is γ1 / γ10 = 8. .014.

  The reverse speed is formed by engaging the clutches C2 and C4 and the brake B2 and releasing the remaining clutches C1 and C3 and the brake B1. That is, when the reverse gear is formed, the second ring gear 22r of the second planetary gear 22 and the third ring gear 23r of the third planetary gear 23 are connected to each other by the clutch C2, and the first planetary gear 21 of the second planetary gear 23 is connected by the clutch C4. The second carrier 22c of the first carrier 21c and the second planetary gear 22 and the fourth ring gear 24r of the fourth planetary gear 24 are connected to each other, and the third ring gear 23r of the third planetary gear 23 is further connected to the transmission case by the brake B2. 11 is fixed so as not to rotate. In the present embodiment, the gear ratio γrev in the reverse speed is γrev = −4.868. The step ratio between the first forward speed and the reverse speed is | γrev / γ1 | = 0.974.

  As described above, according to the automatic transmission 20, the forward speed and the reverse speed from the first speed to the tenth speed can be provided by engaging and disengaging the clutches C1 to C4 and the brakes B1 and B2. As a result, in the automatic transmission 20, since the spread can be increased (8.014 in the present embodiment), the speed ratio of the low speed stage and the speed ratio of the high speed stage are further reduced, It is possible to improve the fuel efficiency of the vehicle on which the automatic transmission 20 is mounted and further improve the acceleration performance of the vehicle. Therefore, according to the automatic transmission 20, it is possible to satisfactorily improve both the fuel consumption of the vehicle on which the automatic transmission 20 is mounted and the drivability, that is, the acceleration performance of the vehicle, the shift feeling, and the like.

  Further, in the automatic transmission 20, the first forward speed is achieved by engaging any three of the six engaging elements, that is, the clutches C1 to C4 and the brakes B1 and B2 and releasing the remaining three. To the tenth forward speed and the reverse speed. Thus, for example, as compared with a transmission that forms a plurality of shift stages by engaging two of the six clutches and brakes and releasing the remaining four, it is released as the shift stages are formed. The number of engaging elements can be reduced. As a result, drag loss due to slight contact between members of the engagement element released with the formation of the shift stage is reduced, and the power transmission efficiency in the automatic transmission 20, that is, the fuel consumption of the vehicle is further improved. It becomes possible to make it.

  Further, in the automatic transmission 20, planetary gears including the first, second, third, or fourth ring gears 21r to 24r are used as the first to fourth planetary gears 21 to 24. As shown in FIG. The first to fourth ring gears 21r to 24r are configured so that the first to fourth ring gears 21r to 24r do not rotate at a high rotational speed when the forward gear and the reverse gear from the first gear to the tenth gear are formed. An increase in inertia during rotation (equivalent inertia with respect to the input shaft 20i) can be suppressed. Thereby, while shortening the time which engagement of each clutch C1-C4 and brake B1, B2 shortens, generation | occurrence | production of the shock at the time of the gear shift accompanying engagement of each clutch C1-C4 and brake B1, B2 is suppressed, Furthermore, it is possible to satisfactorily ensure the durability of the friction materials of the clutches C1 to C4 and the brakes B1 and B2, that is, the friction plates and the separator plates. In addition, by reducing the inertia at the time of rotation of the first to fourth ring gears 21r to 24r, the size (thickness, etc.) associated with securing the strength of the first to fourth ring gears 21r to 24r, that is, an increase in weight or automatic transmission An increase in size of 20 can be suppressed. As a result, in the automatic transmission 20, the speed change performance and the durability of the clutches C1 to C4 and the brakes B1 and B2 can be further improved, and the entire apparatus can be reduced in weight and size.

  Further, by making the first, second, third and fourth planetary gears 21, 22, 23, and 24 into single pinion type planetary gears, compared to the case where these are made into double pinion type planetary gears, for example, While reducing the meshing loss between the rotating elements in the first, second, third and fourth planetary gears 21, 22, 23, 24, the power transmission efficiency in the automatic transmission 20, that is, the fuel efficiency of the vehicle is further improved. It is possible to further improve the assemblability while reducing the number of parts and suppressing the weight increase of the automatic transmission 20.

  In the above-described automatic transmission 20, at least one of the clutches C1 to C4 and the brakes B1 and B2 may be a meshing engagement element such as a dog clutch or a dog brake. For example, in the automatic transmission 20, the clutch C3 engaged from the seventh forward speed to the tenth forward speed and the reverse speed may be a dog clutch, and the first forward speed to the fourth forward speed stage. , And the brake B2 engaged in the reverse gear may be a dog brake. In the automatic transmission 20, the gear ratios λ1 to λ4 in the first to fourth planetary gears 21, 22, 23, and 24 are not limited to those exemplified in the above description. Further, in the automatic transmission 20, at least one of the first, second, third, and fourth planetary gears 21, 22, 23, and 24 may be a double pinion planetary gear.

  As described above, the multi-stage transmission according to the present invention is a multi-stage transmission that shifts the power transmitted to the input member and transmits the power to the output member. The multi-stage transmission is sequentially arranged at intervals corresponding to the gear ratio on the speed diagram. A first planetary gear having a first rotation element, a second rotation element, and a third rotation element, and a fourth rotation element and a fifth rotation element that are sequentially arranged at intervals corresponding to the gear ratio on the velocity diagram. And a second planetary gear having a sixth rotating element and a seventh planetary gear having a seventh rotating element, an eighth rotating element, and a ninth rotating element arranged in order at intervals corresponding to the gear ratio on the velocity diagram A fourth planetary gear having a tenth rotating element, an eleventh rotating element, and a twelfth rotating element arranged in order at intervals corresponding to the gear ratio on the velocity diagram, and the first, second, Any of the rotating elements of the third and fourth planetary gears A first, a second, a third, a fourth, a fifth, and a sixth engaging element for connecting to the rolling element or the stationary member and releasing the connection between them, the fifth rotating element of the second planetary gear Is always connected to the input member, the eighth rotating element of the third planetary gear is always connected to the output member, and the first rotating element of the first planetary gear and the third planetary gear of the third planetary gear are The seventh rotating element is always connected, and the second rotating element of the first planetary gear and the fifth rotating element of the second planetary gear are always connected, and the third planetary gear is the third rotating element. The rotating element and the eleventh rotating element of the fourth planetary gear are always connected, and the fourth rotating element of the second planetary gear and the tenth rotating element of the fourth planetary gear are always connected. The first engagement element is the first planetary gear that is always connected. Connecting the third rotating element and the eleventh rotating element of the fourth planetary gear and the eighth rotating element of the third planetary gear to each other and releasing the connection between them; The sixth rotating element of the second planetary gear and the ninth rotating element of the third planetary gear are connected to each other and are disconnected from each other, and the third engaging element is always connected. Connecting the first rotating element of the first planetary gear and the seventh rotating element of the third planetary gear and the sixth rotating element of the second planetary gear to each other and releasing the connection between them; The fourth engaging element connects the second rotating element of the first planetary gear, the fifth rotating element of the second planetary gear, and the twelfth rotating element of the fourth planetary gear, which are always connected to each other. Connect and release both connections to The coupling element connects the fourth rotating element of the second planetary gear and the tenth rotating element of the fourth planetary gear, which are always connected, to the stationary member so as to be non-rotatable and to release the connection between them. The sixth engaging element connects the ninth rotating element of the third planetary gear to a stationary member so as to be non-rotatable, and releases the connection between the first, second, second, By selectively engaging any three of the third, fourth, fifth and sixth engaging elements, a forward speed and a reverse speed from the first speed to the tenth speed are formed. It is characterized by that.

  In the multi-stage transmission configured as described above, since the spread can be increased, the vehicle in which the multi-stage transmission is mounted by increasing the low-speed gear ratio and decreasing the high-speed gear ratio. As a result, the drivability, that is, the acceleration performance of the vehicle and the like can be further improved. Further, in this multi-stage transmission, when planetary gears including ring gears are used as the first, second, third and fourth planetary gears, the forward gear and the reverse gear from the first gear to the tenth gear are used. It is possible to prevent an increase in inertia during rotation of the ring gear by preventing the ring gear having a particularly large diameter from rotating at a high rotational speed during formation. As a result, the time required for engaging the engaging element is shortened, the occurrence of shock at the time of shifting accompanied by the engagement of the engaging element is suppressed, and the durability of the friction material of the engaging element is improved. Can be secured. As a result, in the multi-stage transmission according to the present invention, it becomes possible to further improve the fuel consumption, drivability, speed change performance, and durability of the engagement element of the vehicle in which the multi-stage transmission is mounted.

Furthermore, in the multi-stage transmission according to the present invention, the forward speed and the reverse speed from the first speed to the tenth speed are formed by engaging the first to sixth engaging elements as follows. Can do. That is, the forward first speed is formed by engaging the third engagement element, the fourth engagement element, and the sixth engagement element. The second forward speed is formed by engaging the third engagement element, the fifth engagement element, and the sixth engagement element. The third forward speed is formed by engaging the fourth engagement element, the fifth engagement element, and the sixth engagement element. The fourth forward speed is formed by engaging the first engagement element, the fifth engagement element, and the sixth engagement element. The fifth forward speed is formed by engaging the first engagement element, the fourth engagement element, and the fifth engagement element. The sixth forward speed is formed by engaging the first engagement element, the third engagement element, and the fifth engagement element. The seventh forward speed is formed by engaging the first engagement element, the second engagement element, and the third engagement element. The eighth forward speed is formed by engaging the first engagement element, the second engagement element, and the fifth engagement element. The ninth forward speed is
It is formed by engaging the second engagement element, the third engagement element, and the fifth engagement element. The tenth forward speed is formed by engaging the second engagement element, the fourth engagement element, and the fifth engagement element. The reverse gear is formed by engaging the second engagement element, the fourth engagement element, and the sixth engagement element.

  As described above, in the multi-stage transmission according to the present invention, any three of the first to sixth engaging elements are engaged and the remaining three are released to advance the first forward speed to the tenth forward speed. And a reverse gear is formed. Accordingly, for example, compared with a transmission that forms a plurality of shift stages by engaging two of the six engagement elements and releasing the remaining four, the release is performed with the formation of the shift stage. The number of engaging elements can be reduced. As a result, drag loss in the engagement element released with the formation of the shift stage can be reduced, and the power transmission efficiency in the multi-stage transmission, that is, the fuel consumption of the vehicle can be further improved.

  The first planetary gear includes a first sun gear, a first ring gear, and a first carrier that rotatably and reciprocally holds a plurality of first pinion gears that mesh with the first sun gear and the first ring gear, respectively. The second planetary gear may include a second sun gear, a second ring gear, and a plurality of second pinion gears meshed with the second sun gear and the second ring gear, respectively. It may be a single pinion type planetary gear having a second carrier that is rotatably and revolved, and the third planetary gear includes a third sun gear, a third ring gear, the third sun gear, and the third gear, respectively. A single carrier having a third carrier for holding a plurality of third pinion gears meshed with the third ring gear so as to be rotatable and revolved; The fourth planetary gear may be a fourth sun gear, a fourth ring gear, and a plurality of fourth pinion gears that mesh with the fourth sun gear and the fourth ring gear, respectively. It may be a single pinion type planetary gear having a fourth carrier that is held so as to be able to revolve, the first rotating element may be the first sun gear, and the second rotating element may be the first rotating gear. The third rotation element may be the first ring gear, the fourth rotation element may be the second sun gear, and the fifth rotation element may be the first rotation gear. The sixth rotating element may be the second ring gear, the seventh rotating element may be the third sun gear, and the eighth rotating element may be the second carrier. 3rd key The ninth rotating element may be the third ring gear, the tenth rotating element may be the fourth sun gear, and the eleventh rotating element may be the first rotating element. There may be four carriers, and the twelfth rotating element may be the fourth ring gear.

  Thus, by making the first, second, third and fourth planetary gears into single pinion type planetary gears, the meshing loss between the rotating elements in the first, second, third and fourth planetary gears is reduced. The power transmission efficiency in the multi-stage transmission, that is, the fuel efficiency of the vehicle can be further reduced, and the number of parts can be reduced to further improve the assembly while suppressing the weight increase of the multi-stage transmission.

  Furthermore, the output member may be a counter drive gear included in a gear train that transmits power to a differential gear connected to a front wheel of the vehicle. That is, the multi-stage transmission according to the present invention may be configured as a transmission mounted on a front wheel drive vehicle.

  And this invention is not limited to the said embodiment at all, and it cannot be overemphasized that a various change can be made within the range of the extension of this invention. Furthermore, the mode for carrying out the invention described above is merely a specific embodiment of the invention described in the column for solving the problem, and is described in the column for means for solving the problem. It is not intended to limit the elements of the invention.

  The present invention can be used in the manufacturing industry of multi-stage transmissions.

  DESCRIPTION OF SYMBOLS 10 Power transmission device, 11 Transmission case, 12 Starting device, 14o One-way clutch, 14p Pump impeller, 14s Stator, 14t Turbine runner, 15 Lock-up clutch, 16 Damper mechanism, 17 Oil pump, 20 Automatic transmission, 20i Input shaft, 21 first planetary gear, 21c first carrier, 21p first pinion gear, 21r first ring gear, 21s first sun gear, 22 second planetary gear, 22c second carrier, 22p second pinion gear, 22r second ring gear, 22s second Sun gear, 23 3rd planetary gear, 23c 3rd carrier, 23p 3rd pinion gear, 23r 3rd ring gear, 23s 3rd sun gear, 24 4th planetary gear, 24c 4th carrier, 24p 4th pinion gear, 24r 4th phosphorus Gear, 24s 4th sun gear, 40 gear train, 41 counter drive gear, 42 counter driven gear, 43 counter shaft, 44 drive pinion gear, 45 diff ring gear, 50 differential gear, 51 drive shaft, B1, B2 brake, C1, C2, C3 , C4 clutch.

Claims (4)

In a multi-stage transmission that shifts the power transmitted to the input member and transmits it to the output member,
A first planetary gear having a first rotating element, a second rotating element, and a third rotating element arranged in order at intervals corresponding to the gear ratio on the velocity diagram;
A second planetary gear having a fourth rotating element, a fifth rotating element, and a sixth rotating element arranged in order at intervals corresponding to the gear ratio on the velocity diagram;
A third planetary gear having a seventh rotating element, an eighth rotating element, and a ninth rotating element arranged in order at intervals corresponding to the gear ratio on the velocity diagram;
A fourth planetary gear having a tenth rotating element, an eleventh rotating element, and a twelfth rotating element arranged in order at intervals corresponding to the gear ratio on the velocity diagram;
The first, second, third and fourth rotating elements of the first, second, third and fourth planetary gears are connected to other rotating elements or stationary members, respectively, and the connection between them is released. And fifth and sixth engaging elements,
The fifth rotating element of the second planetary gear is always connected to the input member;
The eighth rotating element of the third planetary gear is always connected to the output member;
The first rotating element of the first planetary gear and the seventh rotating element of the third planetary gear are always connected,
The second rotating element of the first planetary gear and the fifth rotating element of the second planetary gear are always connected,
The third rotating element of the first planetary gear and the eleventh rotating element of the fourth planetary gear are always connected,
The fourth rotating element of the second planetary gear and the tenth rotating element of the fourth planetary gear are always connected,
The first engagement element includes the always connected third rotation element of the first planetary gear and the eleventh rotation element of the fourth planetary gear, and the eighth rotation element of the third planetary gear. Connect with each other, disconnect both,
The second engaging element connects the sixth rotating element of the second planetary gear and the ninth rotating element of the third planetary gear to each other, and releases the connection between them.
The third engaging element includes the first rotating element of the first planetary gear, the seventh rotating element of the third planetary gear, and the sixth rotating element of the second planetary gear that are always connected. Connect with each other, disconnect both,
The fourth engaging element connects the second rotating element of the first planetary gear, the fifth rotating element of the second planetary gear, and the twelfth rotating element of the fourth planetary gear, which are always connected to each other. Connect and disconnect both,
The fifth engaging element connects the fourth rotating element of the second planetary gear and the tenth rotating element of the fourth planetary gear, which are always connected, to a stationary member and fixes them in a non-rotatable manner. Disconnect
The sixth engaging element connects the ninth rotating element of the third planetary gear to a stationary member and fixes it to be non-rotatable, and releases the connection between them.
Advancement from the first speed to the tenth speed by selectively engaging any three of the first, second, third, fourth, fifth and sixth engagement elements A multi-stage transmission characterized by forming a stage and a reverse stage. The multi-stage transmission according to claim 1, wherein
A forward first speed is formed by engagement of the third engagement element, the fourth engagement element, and the sixth engagement element;
A forward second speed is formed by engagement of the third engagement element, the fifth engagement element, and the sixth engagement element;
A forward third speed is formed by engagement of the fourth engagement element, the fifth engagement element, and the sixth engagement element;
Forward fourth speed is formed by engagement of the first engagement element, the fifth engagement element, and the sixth engagement element;
A forward fifth speed is formed by engagement of the first engagement element, the fourth engagement element, and the fifth engagement element,
A forward sixth speed is formed by engagement of the first engagement element, the third engagement element, and the fifth engagement element,
A forward seventh speed is formed by engagement of the first engagement element, the second engagement element, and the third engagement element,
A forward eighth speed is formed by engagement of the first engagement element, the second engagement element, and the fifth engagement element;
A forward ninth speed is formed by engagement of the second engagement element, the third engagement element, and the fifth engagement element,
The forward tenth speed stage is formed by the engagement of the second engagement element, the fourth engagement element, and the fifth engagement element,
The multi-stage transmission is characterized in that a reverse gear is formed by the engagement of the second engagement element, the fourth engagement element, and the sixth engagement element. The multi-stage transmission according to claim 1 or 2,
The first planetary gear includes a first sun gear, a first ring gear, and a first carrier that holds a plurality of first pinion gears that mesh with the first sun gear and the first ring gear, respectively, in a freely rotating and revolving manner. It is a single pinion type planetary gear,
The second planetary gear includes a second sun gear, a second ring gear, and a second carrier that holds a plurality of second pinion gears that mesh with the second sun gear and the second ring gear, respectively, in a freely rotating and revolving manner. It is a single pinion type planetary gear,
The third planetary gear includes a third sun gear, a third ring gear, and a third carrier that holds a plurality of third pinion gears that mesh with the third sun gear and the third ring gear, respectively, in a freely rotating and revolving manner. It is a single pinion type planetary gear,
The fourth planetary gear includes a fourth sun gear, a fourth ring gear, and a fourth carrier that holds a plurality of fourth pinion gears that mesh with the fourth sun gear and the fourth ring gear, respectively, in a freely rotating and revolving manner. It is a single pinion type planetary gear,
The first rotating element is the first sun gear, the second rotating element is the first carrier, and the third rotating element is the first ring gear;
The fourth rotating element is the second sun gear, the fifth rotating element is the second carrier, and the sixth rotating element is the second ring gear;
The seventh rotating element is the third sun gear, the eighth rotating element is the third carrier, and the ninth rotating element is the third ring gear;
The tenth rotation element is the fourth sun gear, the eleventh rotation element is the fourth carrier, and the twelfth rotation element is the fourth ring gear. The multi-stage transmission according to any one of claims 1 to 3,
The multi-stage transmission, wherein the output member is a counter drive gear included in a gear train that transmits power to a differential gear connected to a front wheel of a vehicle.

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