JP2016070426A - Automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve low cost of the entire device, reduction in weight and efficiency.SOLUTION: An automatic transmission includes: first, second, third planetary gears 21, 22, 23; clutches C1, C2; and brakes B1, B2. Then, a first sun gear 21s is connected to an input shaft 20i, a first carrier 21c and a third carrier 23c are connected to a counter drive gear 41, a first ring gear 21r and a second ring gear 22r are connected, and a second carrier 22c and a third sun gear 23s are connected. Also, the first sun gear 21s and a third ring gear 23r are connected by the clutch C1, a second sun gear 22s and the third ring gear 23r are connected by the clutch C2, the second carrier 22c is connected (fixed) to a transmission case 11 by the brake B1, and the second sun gear 22s is connected (fixed) to the transmission case 11 by the brake B2.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an automatic transmission, and more particularly, to an automatic transmission that shifts power transmitted to an input member and transmits the power to an output member.

  Conventionally, this type of automatic transmission includes a single pinion type first and second planetary gear set, a double pinion type third planetary gear set, first and second clutches, and first and second brakes. The first and second clutches and the first and second brakes are selectively engaged to form a forward speed and a reverse speed from the first speed to the fifth speed. Has been proposed (see, for example, Patent Document 1).

  In this automatic transmission, the ring gear of the first planetary gear set is always connected to the input shaft, and the ring gear of the third planetary gear set is always connected to the output shaft, and the sun gear and the second planetary gear set of the first planetary gear set are connected. Of the first planetary gear set and the carrier of the third planetary gear set are always connected, and the carrier of the second planetary gear set and the sun gear of the third planetary gear set are always connected. . In addition, the first clutch connects the ring gear and the input shaft of the first planetary gear set, the carrier of the first planetary gear set, and the carrier of the third planetary gear set to each other, and releases the connection between them. With the two clutches, the carrier of the first planetary gear set and the carrier of the third planetary gear set and the ring gear of the second planetary gear set are connected to each other and the connection between them is released. The ring gear of the planetary gear set is connected to the casing and fixed to be non-rotatable, and the connection between both is released. The second brake connects the carrier of the second planetary gear set and the sun gear of the third planetary gear set to the casing. Thus, the rotation is fixed and the connection between the two is released. The first forward speed is formed by engagement of the second clutch and the second brake, and the second forward speed is formed by engagement of the first and second brakes. The first clutch and the second brake The forward third speed is formed by engaging the first clutch, the fourth forward speed is formed by engaging the first clutch and the first brake, and the fifth forward speed is formed by engaging the first and second clutches. The reverse gear is formed by the engagement of the second clutch and the first brake.

JP-A-45-5963

  In the above automatic transmission, the rotational speeds of the plurality of pinion gears of the first planetary gear set when the forward gear and the reverse gear are formed are increased (the gear ratio of the first, second, and third planetary gears is 0.639, In the case of 0.585 and -0.454, the maximum speed is about 5.5 times the rotational speed of the input shaft). For this reason, it is necessary to increase the number of bearing rollers interposed between the plurality of pinion gears and the respective pinion shafts, resulting in high cost, mass increase, and deterioration in efficiency of the entire apparatus.

  The main purpose of the automatic transmission of the present invention is to reduce the overall cost, weight and efficiency of the apparatus.

  The automatic transmission according to the present invention employs the following means in order to achieve the main object described above.

The automatic transmission of the present invention is
An automatic 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 that are 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;
1st, 2nd, 3rd, 4th engaging element which connects either one of the rotating elements of said 1st, 2nd, 3rd planetary gear with another rotating element or a stationary member, respectively, and cancels | releases both connection When,
With
The first rotating element of the first planetary gear is always connected to the input member;
The second rotating element of the first planetary gear and the eighth rotating element of the third planetary gear are always connected to the output member;
The third rotating element of the first planetary gear and the sixth rotating element of the second planetary gear are always connected,
The fifth rotating element of the second planetary gear and the seventh rotating element of the third planetary gear are always connected,
The first engaging element connects the first rotating element and the input member of the first planetary gear, which are always coupled, and the ninth rotating element of the third planetary gear, and connects the two together. Is released,
The second engagement element connects the fourth rotation element of the second planetary gear and the ninth rotation element of the third planetary gear to each other and releases the connection between them;
The third engaging element connects the fifth rotating element of the second planetary gear and the seventh rotating element of the third planetary gear that are always connected to the stationary member to fix the non-rotatable together. Disconnect
The fourth engaging element is connected to the stationary member to fix the fourth rotating element of the second planetary gear to be non-rotatable and releases the connection between them.
By selectively engaging any two of the first, second, third and fourth engagement elements, a forward speed and a reverse speed from the first speed to the fifth speed are formed. To
It is characterized by that.

  In the automatic transmission according to the present invention, the first rotating element of the first planetary gear is always connected to the input member, and the second rotating element of the first planetary gear and the eighth rotating element of the third planetary gear are always connected to the output member. Connected, the third rotating element of the first planetary gear and the sixth rotating element of the second planetary gear are always connected, and the fifth rotating element of the second planetary gear and the seventh rotating element of the third planetary gear are always connected. Connected. In addition, the first engaging element connects the first rotating element and the input member of the first planetary gear, which are always connected, and the ninth rotating element of the third planetary gear, and the connection between them is released. . By the second engagement element, the fourth rotation element of the second planetary gear and the ninth rotation element of the third planetary gear are connected to each other and the connection between them is released. By the third engagement element, the fifth rotation element of the second planetary gear and the seventh rotation element of the third planetary gear, which are always connected, are connected to the stationary member and fixed to be non-rotatable, and the connection between them is released. The By the fourth engagement element, the fourth rotation element of the second planetary gear is connected to the stationary member and fixed so as not to rotate, and the connection between the two is released. Then, by selectively engaging any two of the first, second, third and fourth engaging elements, the forward speed and the reverse speed from the first speed to the fifth speed can be achieved. Form. By setting it as such a structure, it can suppress that the rotational speed of several 1st, 2nd, 3rd pinion gears of a 1st, 2nd, 3rd planetary gear becomes large. As a result, the number of bearing rollers interposed between the plurality of first, second and third pinion gears and each pinion shaft can be reduced, and the overall cost of the apparatus is reduced, the weight is reduced, and the efficiency is improved. be able to. In addition, when the rotational speeds of the plurality of first, second, and third pinion gears are increased, a special heat treatment process is performed when manufacturing the first, second, and third pinion shafts in order to ensure high durability. The first, second, and third pinions are suppressed by preventing the rotation speed of the plurality of first, second, and third pinion gears from increasing. It is possible to suppress the need for a special heat treatment process or the like when manufacturing the shaft, thereby suppressing complication of the manufacturing process.

It is a schematic block diagram of the power transmission device 10 provided with the automatic transmission 20 as an automatic transmission which concerns on one Embodiment of this invention. It is a speed diagram which shows ratio of the rotational speed of each rotation element with respect to the rotational speed (input rotational speed) of the input shaft 20i in the automatic transmission 20 of this embodiment. 3 is an operation table showing the relationship between each gear position in the automatic transmission 20 and the operating states of clutches C1, C2 and brakes B1, B2. FIG. 6 is an explanatory diagram showing the relationship between each gear position in the automatic transmission 20 and the rotation speeds of first, second, and third pinion gears 21p, 22p, and 23p. It is a schematic block diagram of the power transmission device 10B provided with the automatic transmission 20B as an automatic transmission which concerns on other embodiment of this invention.

  Next, the form for implementing this invention is demonstrated using an Example.

  FIG. 1 is a schematic configuration diagram of a power transmission device 10 including an automatic transmission 20 as an automatic transmission according to an embodiment of the present invention. A power transmission device 10 shown in the figure 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 transmits power (torque) from the engine. It can be transmitted to left and right front wheels (drive wheels) (not shown). As shown in the figure, the power transmission device 10 includes a transmission case in addition to the automatic transmission 20 that shifts the power transmitted from the engine to an input shaft 20i as an input member and transmits it to a counter drive gear 41 as an output member. (Stationary member) 11, starting device (fluid transmission device) 12, oil pump 17, and the like.

  The starting device 12 includes an input-side pump impeller 14p connected to a drive source, an output-side turbine runner 14t, a pump impeller 14p, and a turbine runner 14t connected to an input shaft (input member) 20i of the automatic transmission 20. A stator 14s that is disposed on the inside and rectifies the flow of hydraulic oil from the turbine runner 14t to the pump impeller 14p, and a one-way clutch 14o that is supported by a stator shaft (not shown) and restricts the rotational direction of the stator 14s in one direction. A torque converter is provided. Further, the starting device 12 connects a front cover connected to an engine crankshaft and the like and the input shaft 20i of the automatic transmission 20 to each other, and releases the connection between the lockup clutch 15 and the front cover and the automatic transmission. And a damper mechanism 16 that attenuates vibration between the input shaft 20 i of the machine 20. The starting device 12 may have a fluid coupling that does not have the stator 14s.

  The oil pump 17 includes a pump assembly having 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 five-speed transmission, and as shown in FIG. 1, in addition to an input shaft 20i as an input member, a counter drive gear 41 as an output member, an automatic transmission 20 (input shaft 20 i), a single pinion type first planetary gear 21, a single pinion type second planetary gear 22, and a single pinion type third planetary gear 23 arranged side by side in the axial direction. Further, the automatic transmission 20 includes a clutch C1 (first clutch) as a first engagement element and a clutch C2 as a second engagement element for changing a power transmission path from the input shaft 20i to the counter drive gear 41. (Second clutch), a brake B1 (first brake) as a third engagement element, and a brake B2 (second brake) as a fourth engagement element. 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. A gear train 40 having a coupled 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 coupled to the differential ring gear 45, and a drive shaft 51. To the left and right front wheels.

  In the present embodiment, the first, second and third planetary gears 21, 22 and 23 are connected to the first planetary gear 21, the third planetary gear 23 and the second planetary gear 21 from the starting device 12, that is, the engine side (left side in FIG. 1). It arrange | positions in the transmission case 11 so that the planetary gear 22 may be located in order. In addition, for example, the clutches C1 and C2 are disposed between the first planetary gear 21 and the third planetary gear 23, and the brakes B1 and B2 are opposite to the third planetary gear 23 with respect to the second planetary gear 22. Placed on the side.

  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. A plurality of first pinion gears 21p meshing with each other, and a plurality of first pinion gears 21p that are inserted through needle bearings into the plurality of first pinion gears 21p, respectively, thereby rotating (rotating) the plurality of first pinion gears 21p. And a first carrier 21c that is held so as to be freely revolved. In the present embodiment, the gear ratio 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) λ1 is set to λ1 = 0.650, 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. A plurality of second pinion gears 22p meshing with each other, and a plurality of second pinion gears 22p inserted through needle bearings into the plurality of second pinion gears 22p, respectively, thereby rotating the plurality of second pinion gears 22p (rotating) And a second carrier 22c that is held so as to be freely revolved. In the present embodiment, the gear ratio 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) λ2 is set to λ2 = 0.650, 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. A plurality of third pinion gears 23p that are engaged with each other, and a plurality of third pinion gears 23p that are inserted through needle bearings in the plurality of third pinion gears 23p, respectively, to rotate (rotate) the plurality of third pinion gears 23p. ) And a third carrier 23c that revolves freely. In the present embodiment, the gear ratio 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) λ3 is set to λ3 = 0.650, for example.

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

  The clutch C1 connects the first sun gear 21s and the input shaft 20i of the first planetary gear 21 that are always connected to the third ring gear 23r of the third planetary gear 23 and releases the connection therebetween. . The clutch C2 connects the second sun gear 22s of the second planetary gear 22 and the third ring gear 23r of the third planetary gear 23 to each other and releases the connection between them. The brake B1 non-rotatably connects (fixes) the second carrier 22c of the second planetary gear 22 and the third sun gear 23s of the third planetary gear 23 that are always connected to the transmission case 11 as a stationary member. The second carrier 22c and the third sun gear 23s are released so as to be rotatable with respect to the transmission case 11. The brake B2 connects (fixes) the second sun gear 22s of the second planetary gear 22 to the transmission case 11 in a non-rotatable manner and releases the second sun gear 22s to the transmission case 11 so as to be rotatable. .

  In the present embodiment, the clutches C1 and C2 include 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 in which both surfaces are formed smoothly. And a multi-plate friction type hydraulic clutch (friction engagement element) having a hydraulic servo constituted by an engagement oil chamber to which hydraulic oil is supplied, a centrifugal hydraulic pressure cancellation chamber, and the like. 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 and C2 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 of the present embodiment. FIG. 4 is an operation table showing the relationship between the respective gear speeds and the operating states of the clutches C1, C2 and brakes B1, B2. FIG. 4 shows the respective gear speeds in the automatic transmission 20 and the first, second and third pinion gears 21p, It is explanatory drawing which shows the relationship with the rotational speed of 22p, 23p. In FIG. 2, the rotational speed of the input shaft 20i, that is, the first sun gear 21s is set to 1. In FIG. 4, the rotational speeds of the first, second, and third pinion gears 21p, 22p, and 23p are values when the rotational speed of the input shaft 20i is 1.

  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). According to the order of arrangement in the speed diagram, in the present embodiment, 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 ring gear is used. 21 r 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 corresponding to the gear ratio λ1 on the velocity diagram.

  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 speed 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 at an interval corresponding to the gear ratio λ2 on the central speed diagram). According to the order of arrangement in the velocity diagram, in the present embodiment, 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 ring gear. 22r is a sixth rotating element of the automatic transmission 20. Therefore, 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 corresponding 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). On the rightmost speed diagram), the third 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. According to the order of arrangement in the speed diagram, in the present embodiment, 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 ring gear. 23r is a 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 arranged in order at intervals corresponding to the gear ratio λ3 on the velocity diagram.

  In the automatic transmission 20, the input members are changed by engaging or releasing the clutches C 1 and C 2 and the brakes B 1 and B 2 as shown in FIG. 3 to change the connection relationship of the first to ninth rotating elements. Between the input shaft 20i as the output member and the counter drive gear 41 as the output member, there are five power transmission paths in the forward rotation direction and one in the reverse rotation direction, that is, advance from the first speed to the fifth speed. Steps and reverse steps can be formed.

  Specifically, the forward first speed is formed by engaging the clutch C2 and the brake B1 and releasing the clutch C1 and the brake B2. That is, when the first forward speed is established, the second sun gear 22s 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 are always connected by the brake B1. The second carrier 22c of the second planetary gear 22 and the third sun gear 23s of the third planetary gear 23 are non-rotatably connected (fixed) to the transmission case 11. In this embodiment (when the gear ratios λ1 to λ3 of the first to third planetary gears 21 to 23 are λ1 = 0.650, λ2 = 0.650, λ3 = 0.650, the same applies hereinafter) The gear ratio (the rotational speed of the input shaft 20i / the rotational speed of the counter drive gear 41) γ1 at the high speed is γ1 = 4.188. Further, the rotational speeds of the first, second, and third pinion gears 21p, 22p, and 23p when the forward first speed is formed are as shown in FIG.

  The second forward speed is formed by engaging the brakes B1 and B2 and releasing the clutches C1 and C2. That is, when the second forward speed is established, the brake B1 prevents the second carrier 22c of the second planetary gear 22 and the third sun gear 23s of the third planetary gear 23 that are always connected to rotate with respect to the transmission case 11. The second sun gear 22s of the second planetary gear 22 is non-rotatably connected (fixed) to the transmission case 11 by the brake B2. In the present embodiment, the gear ratio γ2 at the second forward speed is γ2 = 2.538. Further, the step ratio γ1 / γ2 between the first forward speed and the second forward speed is γ1 / γ2 = 1.650. Furthermore, the rotational speeds of the first, second, and third pinion gears 21p, 22p, and 23p when the second forward speed is formed are as shown in FIG.

  The third forward speed is formed by engaging the clutch C1 and the brake B1 and releasing the clutch C2 and the brake B2. That is, when the third forward speed is established, the clutch C1 connects the first sun gear 21s and the input shaft 20i of the first planetary gear 21 and the third ring gear 23r of the third planetary gear 23 that are always connected. The second carrier 22c of the second planetary gear 22 and the third sun gear 23s of the third planetary gear 23, which are always connected, are non-rotatably connected (fixed) to the transmission case 11 by the brake B1. In the present embodiment, the gear ratio γ3 at the third forward speed is γ3 = 1.650. The step ratio γ2 / γ3 between the second forward speed and the third forward speed is γ2 / γ3 = 1.538. Furthermore, the rotational speeds of the first, second, and third pinion gears 21p, 22p, and 23p when the third forward speed is formed are as shown in FIG.

  The fourth forward speed is formed by engaging the clutch C1 and the brake B2 and releasing the clutch C2 and the brake B1. That is, when the fourth forward speed is established, the clutch C1 connects the first sun gear 21s and the input shaft 20i of the first planetary gear 21 and the third ring gear 23r of the third planetary gear 23 that are always connected. The second sun gear 22s of the second planetary gear 22 is non-rotatably connected (fixed) to the transmission case 11 by the brake B2. In the present embodiment, the gear ratio γ4 at the fourth forward speed is γ4 = 1.344. The step ratio γ3 / γ4 between the third forward speed and the fourth forward speed is γ3 / γ4 = 1.228. Furthermore, the rotational speeds of the first, second, and third pinion gears 21p, 22p, and 23p when the forward fourth speed is formed are as shown in FIG.

  The fifth forward speed is formed by engaging the clutches C1 and C2 and releasing the brakes B1 and B2. That is, when the fifth forward speed is established, the first sun gear 21s and the input shaft 20i of the first planetary gear 21 and the third ring gear 23r of the third planetary gear 23 are always connected to each other by the clutch C1. The second sun gear 22s 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. In the present embodiment, the gear ratio γ5 at the fifth forward speed is γ5 = 1.000. The step ratio γ4 / γ5 between the fourth forward speed and the fifth forward speed is γ4 / γ5 = 1.344. The spread in the automatic transmission 20 (gear ratio width = gear ratio γ1 of the forward first speed that is the lowest gear stage / gear ratio γ5 of the forward fifth speed that is the highest gear stage) is γ1 / γ5 = 4. .188. The rotational speeds of the first, second, and third pinion gears 21p, 22p, and 23p when the forward fifth speed is formed are as shown in FIG.

  The reverse speed is formed by engaging the clutch C2 and the brake B2 and releasing the clutch C1 and the brake B1. That is, when the reverse gear is formed, the second sun gear 22s 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 planetary gear 22 of the second planetary gear 22 is connected by the brake B2. The second sun gear 22s is connected (fixed) to the transmission case 11 so as not to rotate. In the present embodiment, the gear ratio γrev in the reverse speed is γrev = −3.905. Further, the step ratio | γrev / γ1 | between the first forward speed and the reverse speed is γrev / γ1 = 0.932. Furthermore, the rotational speeds of the first, second, and third pinion gears 21p, 22p, and 23p when the reverse gear is formed are as shown in FIG.

  Thus, in the automatic transmission 20 of the present embodiment, the forward speed and the reverse speed from the first speed to the fifth speed are formed by the engagement and release of the clutches C1 and C2 and the brakes B1 and B2. be able to.

  In the automatic transmission 20, as shown in FIG. 4, the rotational speeds of the first, second, and third pinion gears 21p, 22p, and 23p of the first, second, and third planetary gears 21, 22, and 23 are set as follows. When the forward gear is formed and when the reverse gear is formed, the rotational speed of the input shaft 20i can be reduced to about 2.8 times or less and about 4.7 times or less, respectively. Thereby, the number of rollers of each needle bearing interposed between each of the first, second and third pinion gears 21p, 22p and 23p and each of the first, second and third pinion shafts 21ps, 22ps and 23ps is reduced. Thus, the overall cost of the apparatus can be reduced, the weight can be reduced, and the efficiency can be improved. Further, the first, second and third planetary gears 21 and 22 are secured to ensure high durability by suppressing the rotation speed of the first, second and third pinion gears 21p, 22p and 23p from increasing. , 23 can be prevented from requiring a special heat treatment process when manufacturing the first, second and third pinion shafts 21ps, 22ps, and 23ps, and the manufacturing process can be prevented from becoming complicated.

  Further, in the automatic transmission 20, as shown in FIG. 1, the first, second, and third planetary gears 21, 22, and 23 are configured as single-pinion type planetary gears. As a result, the automatic transmission can reduce the meshing loss between the rotating elements in the first, second and third planetary gears 21, 22, and 23 as compared with those configured as, for example, a double pinion type planetary gear. As a result, the power transmission efficiency in the engine 20 can be further improved, and the number of parts can be reduced to improve the assembly while suppressing an increase in weight and size of the automatic transmission 20.

  The automatic transmission 20 of the present embodiment described above includes first, second, and third planetary gears 21, 22, 23, clutches C1, C2, and brakes B1, B2. The first sun gear 21s of the first planetary gear 21 is always connected to an input shaft 20i as an input member, and the first carrier 21c of the first planetary gear 21 and the third carrier 23c of the third planetary gear 23 are used as output members. The first ring gear 21r of the first planetary gear 21 and the second ring gear 22r of the second planetary gear 22 are always connected, and the second carrier 22c of the second planetary gear 22 is connected to the third carrier gear 22c of the second planetary gear 22. The third sun gear 23s of the planetary gear 23 is always connected. The clutch C1 connects the first sun gear 21s and the input shaft 20i of the first planetary gear 21 and the third ring gear 23r of the third planetary gear 23 that are always connected to each other and the connection between them is released. The second sun gear 22s of the second planetary gear 22 and the third ring gear 23r of the third planetary gear 23 are connected to each other and released from each other by the clutch C2, and are always connected by the brake B1. The second carrier 22c of the second planetary gear 22 and the third sun gear 23s of the third planetary gear 23 are connected to the transmission case 11 so as to be non-rotatable and disconnected from each other. The second sun gear 22s of the gear 22 is connected to the transmission case 11 and is fixed so as not to rotate. Connection is released. Thereby, it can suppress that the rotational speed of the 1st, 2nd, 3rd pinion gear 21p, 22p, 23p of the 1st, 2nd, 3rd planetary gears 21, 22, 23 becomes large. As a result, the number of rollers of the needle bearings interposed between the first, second and third pinion gears 21p, 22p and 23p and the first, second and third pinion shafts 21ps, 22ps and 23ps is reduced. Thus, the overall cost of the apparatus can be reduced, the weight can be reduced, and the efficiency can be improved. Further, it is possible to suppress the necessity of a special heat treatment process when manufacturing the first, second, and third planetary gears 21, 22, and 23, and to suppress the complication of the manufacturing process.

  FIG. 5 is a schematic configuration diagram of a power transmission device 10B including an automatic transmission 20B as an automatic transmission according to another embodiment of the present invention. A power transmission device 10B shown in the figure is connected to a crankshaft of an engine (internal combustion engine) (not shown) as a drive source mounted vertically in a front portion of a rear wheel drive vehicle and power (torque) from the engine. Can be transmitted to left and right rear wheels (drive wheels) (not shown). The automatic transmission 20B of the power transmission device 10B corresponds to a modification of the automatic transmission 20 of the power transmission device 10 for a rear wheel drive vehicle. In the automatic transmission 20B, an output shaft 20o as an output member is connected to the left and right rear wheels via a differential gear and a drive shaft (not shown). Thus, the automatic transmission of the present invention may be configured as a transmission mounted on a rear wheel drive vehicle.

  In the above-described automatic transmissions 20 and 20B, the clutches C1 and C2 and the brakes B1 and B2 are configured as friction engagement elements (hydraulic clutches and hydraulic brakes), but at least one of them is an engagement element ( Dog clutch, dog brake). For example, in the automatic transmissions 20 and 20B, the clutch C2 that is engaged when the first forward speed, the fifth forward speed, and the reverse speed are formed, and the first transmission speed to the third forward speed are continuously generated. Thus, the brake B1 to be engaged may be configured as a dog clutch or a dog brake.

  In the above-described automatic transmissions 20 and 20B, the above-described values are used as the gear ratios λ1, λ2, and λ3 in the first, second, and third planetary gears 21, 22, and 23. λ3 is not limited to this value.

  In the automatic transmissions 20 and 20B described above, the first, second, and third planetary gears 21, 22, and 23 are configured as single-pinion type planetary gears, but at least one is a double-pinion type planetary gear. It may be configured as a gear.

  Next, the automatic transmission of the present invention will be described.

  The automatic transmission according to the present invention is an automatic transmission that shifts the power transmitted to the input member and transmits the power to the output member. The first transmission is arranged in order at intervals corresponding to the gear ratio on the speed diagram. A first planetary gear having a rotating element, a second rotating element, and a third rotating element; 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 second planetary gear having a rotating element, and 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. 1st, 2nd, 3rd, 4th engagement for connecting one of the rotating elements of the first, second and third planetary gears to another rotating element or stationary member and releasing the connection between them An element, and the first rotating element of the first planetary gear is always connected to the input member. The second rotating element of the first planetary gear and the eighth rotating element of the third planetary gear are always connected to the output member, and the third rotating element of the first planetary gear and the second planetary gear. The sixth rotating element of the gear is always connected, and the fifth rotating element of the second planetary gear and the seventh rotating element of the third planetary gear are always connected, and the first engaging element Connects the first rotating element and the input member of the first planetary gear, which are always connected, and the ninth rotating element of the third planetary gear, and releases the connection between them, The second engagement element connects the fourth rotation element of the second planetary gear and the ninth rotation element of the third planetary gear to each other and releases the connection therebetween, and the third engagement element Is the fifth rotating element of the second planetary gear always connected And the seventh rotating element of the third planetary gear is connected to the stationary member to be fixed to be non-rotatable and the connection between both is released, and the fourth engaging element is the fourth planetary gear of the second planetary gear. A rotating element is connected to the stationary member and fixed to be non-rotatable, and the connection between both is released, and any two of the first, second, third and fourth engaging elements are selectively engaged. Thus, a forward speed and a reverse speed from the first speed to the fifth speed are formed.

  In the automatic transmission according to the present invention, the first rotating element of the first planetary gear is always connected to the input member, and the second rotating element of the first planetary gear and the eighth rotating element of the third planetary gear are always connected to the output member. Connected, the third rotating element of the first planetary gear and the sixth rotating element of the second planetary gear are always connected, and the fifth rotating element of the second planetary gear and the seventh rotating element of the third planetary gear are always connected. Connected. In addition, the first engaging element connects the first rotating element and the input member of the first planetary gear, which are always connected, and the ninth rotating element of the third planetary gear, and the connection between them is released. . By the second engagement element, the fourth rotation element of the second planetary gear and the ninth rotation element of the third planetary gear are connected to each other and the connection between them is released. By the third engagement element, the fifth rotation element of the second planetary gear and the seventh rotation element of the third planetary gear, which are always connected, are connected to the stationary member and fixed to be non-rotatable, and the connection between them is released. The By the fourth engagement element, the fourth rotation element of the second planetary gear is connected to the stationary member and fixed so as not to rotate, and the connection between the two is released. Then, by selectively engaging any two of the first, second, third and fourth engaging elements, the forward speed and the reverse speed from the first speed to the fifth speed can be achieved. Form. By setting it as such a structure, it can suppress that the rotational speed of several 1st, 2nd, 3rd pinion gears of a 1st, 2nd, 3rd planetary gear becomes large. As a result, the number of bearing rollers interposed between the plurality of first, second and third pinion gears and each pinion shaft can be reduced, and the overall cost of the apparatus is reduced, the weight is reduced, and the efficiency is improved. be able to. In addition, when the rotational speeds of the plurality of first, second, and third pinion gears are increased, a special heat treatment process is performed when manufacturing the first, second, and third pinion shafts in order to ensure high durability. The first, second, and third pinions are suppressed by preventing the rotation speed of the plurality of first, second, and third pinion gears from increasing. It is possible to suppress the need for a special heat treatment process or the like when manufacturing the shaft, thereby suppressing complication of the manufacturing process.

  In such an automatic transmission of the present invention, the first forward speed is formed by the engagement of the second engagement element and the third engagement element, and the third engagement element and the fourth engagement element are The second forward speed is formed by the engagement of the first engagement element, and the third forward speed is formed by the engagement of the first engagement element and the third engagement element, and the first engagement element and the fourth A forward fourth speed is formed by engagement with the engagement element, and a forward fifth speed is formed by engagement of the first engagement element and the second engagement element, and the second engagement element Further, the reverse stage can be formed by the engagement of the fourth engagement element.

  In the automatic transmission according to the present invention, the first planetary gear can rotate and revolve a first sun gear, a first ring gear, and a plurality of first pinion gears meshed with the first sun gear and the first ring gear, respectively. A first pinion type planetary gear having a first carrier held by the second carrier, wherein the second planetary gear is a second sun gear, a second ring gear, and a plurality of meshes with the second sun gear and the second ring gear, respectively. And a second carrier that holds the second pinion gear so as to rotate and revolve. The third planetary gear includes a third sun gear, a third ring gear, and the third sun gear. And a third carrier for holding a plurality of third pinion gears meshing with the third ring gear so as to rotate and revolve. A planetary gear of a gulpinion type, wherein the first rotating element is the first sun gear, the second rotating element is the first carrier, the third rotating element is the first ring gear, and the fourth The rotating element is the second sun gear, the fifth rotating element is the second carrier, the sixth rotating element is the second ring gear, the seventh rotating element is the third sun gear, The eighth rotating element may be the third carrier, and the ninth rotating element may be the third ring gear.

  In this way, by configuring the first, second, and third planetary gears as single pinion type planetary gears, the meshing loss between the rotating elements is reduced, and the power transmission efficiency in the automatic transmission is improved. At the same time, the number of parts can be reduced to improve assembly while suppressing an increase in the weight and size of the automatic transmission.

  Furthermore, in the automatic transmission according to the present invention, 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. The member may be an output shaft connected to the rear wheel of the vehicle via a differential gear. That is, the automatic transmission according to the present invention may be configured as a transmission mounted on a front-wheel drive vehicle or may be configured as a transmission mounted on a rear-wheel drive vehicle.

  Next, 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 20 i corresponds to an “input member”, the counter drive gear 41 and the output shaft 20 o correspond to an “output member”, the first planetary gear 21 corresponds to a “first planetary gear”, and The first sun gear 21s corresponds to the “first rotating element”, the first carrier 21c corresponds to the “second rotating element”, the first ring gear 21r corresponds to the “third rotating element”, and the second planetary gear 22 The second sun gear 22s corresponds to the “fourth rotating element”, the second carrier 22c corresponds to the “fifth rotating element”, and the second ring gear 22r corresponds to the “sixth rotating element”. The third planetary gear 23 corresponds to the “third planetary gear”, the third sun gear 23 s corresponds to the “seventh rotating element”, and the third carrier 23 c corresponds to the “eighth rotating element”. The third ring gear 23r corresponds to the “ninth rotating element” and The switch C1 corresponds to the “first engagement element”, the clutch C2 corresponds to the “second engagement element”, the brake B1 corresponds to the “third engagement element”, and the brake B2 corresponds to the “fourth engagement element”. It corresponds to "combined element".

  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. Therefore, the elements of the invention described in the column of means for solving the problems are not limited. That is, the interpretation of the invention described in the column of means for solving the problem should be made based on the description of the column, and the embodiment of the invention described in the column of means for solving the problem is described. It is only a specific example.

  As mentioned above, although the form for implementing this invention was demonstrated, this invention is not limited to such embodiment at all, and it can implement with a various form in the range which does not deviate from the summary of this invention. Of course.

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

  10, 10B 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, 20B Automatic transmission, 20i input shaft, 20o output shaft, 21 first planetary gear, 21c first carrier, 21p first pinion gear, 21ps first pinion shaft, 21r first ring gear, 21s first sun gear, 22 second planetary gear, 22c second carrier 22p second pinion gear, 22ps second pinion shaft, 22r second ring gear, 22s second sun gear, 23 third planetary gear, 23c third carrier, 23p third pinion gear, 23ps third pinion shaft, 23r 3rd ring gear, 23s 3rd 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 clutch.

Claims (5)

An automatic 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 that are 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;
1st, 2nd, 3rd, 4th engaging element which connects either one of the rotating elements of said 1st, 2nd, 3rd planetary gear with another rotating element or a stationary member, respectively, and cancels | releases both connection When,
With
The first rotating element of the first planetary gear is always connected to the input member;
The second rotating element of the first planetary gear and the eighth rotating element of the third planetary gear are always connected to the output member;
The third rotating element of the first planetary gear and the sixth rotating element of the second planetary gear are always connected,
The fifth rotating element of the second planetary gear and the seventh rotating element of the third planetary gear are always connected,
The first engaging element connects the first rotating element and the input member of the first planetary gear, which are always coupled, and the ninth rotating element of the third planetary gear, and connects the two together. Is released,
The second engagement element connects the fourth rotation element of the second planetary gear and the ninth rotation element of the third planetary gear to each other and releases the connection between them;
The third engaging element connects the fifth rotating element of the second planetary gear and the seventh rotating element of the third planetary gear that are always connected to the stationary member to fix the non-rotatable together. Disconnect
The fourth engaging element is connected to the stationary member to fix the fourth rotating element of the second planetary gear to be non-rotatable and releases the connection between them.
By selectively engaging any two of the first, second, third and fourth engagement elements, a forward speed and a reverse speed from the first speed to the fifth speed are formed. To
An automatic transmission characterized by that. The automatic transmission according to claim 1,
The forward first speed is formed by the engagement of the second engagement element and the third engagement element,
The forward second speed is formed by the engagement of the third engagement element and the fourth engagement element,
A forward third speed is formed by the engagement of the first engagement element and the third engagement element,
A forward fourth speed is formed by engagement of the first engagement element and the fourth engagement element,
A forward fifth speed is formed by the engagement of the first engagement element and the second engagement element,
A reverse gear is formed by the engagement of the second engagement element and the fourth engagement element.
An automatic transmission characterized by that. The automatic 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, so as to rotate and revolve. 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, so as to rotate and revolve. 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, so as to rotate and revolve. 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;
An automatic transmission characterized by that. An automatic transmission according to any one of claims 1 to 3,
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.
An automatic transmission characterized by that. An automatic transmission according to any one of claims 1 to 3,
The output member is an output shaft connected to the rear wheel of the vehicle via a differential gear.
An automatic transmission characterized by that.

Images