JPH02146348A - Automatic transmission - Google Patents

Abstract

PURPOSE:To absorb a speed change shock by arranging three-row simple planet gear sets further connecting the first carrier and the second ring gear through the third clutch to the third sun gear further connected to a fixed part through a one-way clutch. CONSTITUTION:Three-row simple planet gear sets 110, 120, 130 are arranged coaxially with input and output shafts 240, 700, while even the first and second clutches 11, 12, controlling an input, are arranged concentrating. A sun gear 131 of the third-row gear set 130, acting as a reduction gear, is connected to the second ring gear 125 and the first carrier 113 through the third clutch 13 with the first ring gear 115 connected to the second carrier 123 and the third ring gear 135 further with the third sun gear 131 connected to a fixed part through a one-way clutch 32. Thus enabling size to be reduced in the axial direction while a gear train to be constituted rational in strength, while by the one-way clutch, a speed change shock to a 1st speed from the neutral can be absorbed.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an automatic transmission equipped with a starting device and a planetary gear device.

[Prior Art] An automatic transmission that uses a starting device and a three-row simple planetary gear set to achieve four forward speeds and one reverse speed is disclosed in, for example, US Pat. No. 3,483,771.

The one described in the above publication uses three brakes, two clutches, and one one-way clutch as frictional engagement elements, and the three-row simple planetary gear set has axial There is one brake between the first and second rows, and two clutches, one brake, and one one-way brake between the second and third rows. It has a structure in which a clutch is provided and one brake is provided on the outer periphery of the third row.

The input is given to one sun gear of the simple planetary gear set in the first row, and the output is taken out from the carrier in the third row. The sun gear shaft portion of the second row has a triple shaft structure.

This device requires only a small number of frictional engagement elements to achieve four forward speeds and one reverse speed, but on the other hand, as is clear from the engagement state of the frictional engagement elements that operate at each gear, it is possible to achieve 2nd speed and 1 reverse speed. 3
When changing gears between 3rd and 4th speeds, it is necessary to engage another frictional engagement element in synchronization with disengaging one frictional engagement element. A complicated control device is required to switch two frictional engagement elements at the same time.
This was also a factor in increasing costs.

[Problem M to be solved by the invention] Therefore, in the present invention, the three-row simple planetary gear set is arranged in a concentrated manner, and the frictional engagement elements are also arranged in a concentrated manner to shorten the axial dimension and reduce friction. To provide an automatic transmission with four forward speeds and one reverse speed, which simplifies control by avoiding simultaneous switching control of engaging elements as much as possible, and utilizes a one-way clutch to absorb shift shock and achieve smooth shift. .

[Means for Solving the Problems] In order to solve the above-mentioned problems, an automatic transmission of the present invention includes a three-row simple planetary gear set (110, 120, 130) that is arranged collectively.

3-row simple planetary gear set and starting device (2)
the first and second clutches (11, 12) disposed between the input shaft (240) that transmits the output of ) connecting the first intermediate shaft (500
), and a first clutch (12) that connects the second clutch (12) and the sun gear (111) of the first row of simple planetary gear sets.
a second intermediate shaft (600) disposed concentrically on the outer periphery of the intermediate shaft (500), and an output shaft (700) connected to the carrier (133) of the third row simple planetary gear set.
).

The first row of carriers (113) are connected to the second row of ring gears (113).
25) and the third row sun gear (131) via the third clutch (13), the first row ring gear (115) is connected to the second row carrier (123) and the third row sun gear (131). It has a configuration in which it is connected to a ring gear (135) and a third row sun gear (131) is connected to a fixed part via a one-way clutch (32).

[Function] With the above configuration, the three rows of simple planetary gear sets (110, 120, 130) are arranged together, and the first clutch (11) and second clutch (12) that control input are also integrated. and arrange it to achieve a rational arrangement structure. The sun gear (13) of the third row simple planetary gear set (130) acts as a speed reducer.
1), a one-way clutch (32) is interposed in the path that supports the shift gear shift shock using the mechanical shock-absorbing effect of the one-way clutch (32).

Note that the above-mentioned symbols in parentheses are in contrast to the drawings, but do not limit the configuration in any way.

[Example] Hereinafter, the present invention will be explained in detail based on the drawings.

FIG. 2 shows a skeleton of an automatic transmission embodying the present invention, and the automatic transmission, designated as a whole by reference numeral 1, includes a starting device 2 and a transmission 3. As shown in FIG.

The starting device 2 is a fluid transmission device, and includes a rear cover 204. A turbine runner 208 , which has a pump impeller 206 formed on the inner circumferential wall surface of the rear cover 204 and is disposed opposite to the pump impeller 206 , is held by a turbine shell 210 , and is held by a turbine shell 210 .
0 is connected at its inner peripheral portion to an input shaft 240 that is an output member of the starting device M2 and an input member of the transmission 3.

A stator 214 is disposed between the pump impeller 206 and the turbine runner 208, and the inner peripheral portion of the stator 214 is connected to the seventh outer race of the one-way clutch 216, and the inner race of the one-way clutch 216 is a fixed member. It is attached to the outer periphery of a certain support shaft 230. A lock-up clutch 220 that directly connects the front cover 202 and the turbine shell 210 is disposed between the front cover 202 and the turbine shell 210.

The input shaft 240 of the transmission 3 is connected to a clutch drum, which is generally designated by the reference numeral 400.
A clutch 11 is provided. Another drum 470 is disposed behind the clutch drum 400 (hereinafter, the engine side will be referred to as the front, and the side far from the engine will be referred to as the rear), and a second clutch is installed between the hub 445 that connects the clutch drum 470 and the drum 400. 12 will be installed. A band-type first brake 21 for controlling the forward gear is provided on the outer periphery of the drum 470.

The hub of the first clutch 11 is connected to the front end of a first intermediate shaft 500 disposed at the axial center of the transmission 3. The front end of the first intermediate shaft 500 is supported by the rear end of the input shaft 240,
The rear end of the first intermediate shaft 500 is supported by the front end of an output shaft 700, which will be described later.

The outer circumferential portion of the first intermediate shaft 500 supports the inner circumferential portion of the second intermediate shaft 600 coaxially disposed at two fulcrums. Therefore, the intermediate shaft has a double shaft structure.

Drum 47 of second clutch 12 and first brake 21
0 is the second intermediate shaft 600 via the inner cylinder 480
is connected to the front end of the

A planetary gear device is arranged in a concentrated manner on the outer periphery of the connecting portion between the intermediate shaft and the output shaft. The planetary gear device has a simple planetary gear set with three rows, and the first row from the front side of the transmission 3,
They are arranged in the order of the second column and the third column.

The sun gear 111 of the first row of simple planetary gear sets 110 is connected to the second intermediate shaft 600 and meshes with the pinion 112 . One end of the carrier shaft 113 is connected to a ring gear 125 of a second row of simple planetary gear sets 120 via a first connecting member 150,
Furthermore, it is connected to the outer race of the first one-way clutch 31 and the hub of the third clutch 13 via a second connecting member 160. A multi-plate third brake 23 is disposed on the outer periphery of the connecting member 150.

The rear end of the first intermediate shaft 500 is connected to a sun gear 121 of a second row of simple planetary gear sets, and this second row sun gear 121 has a larger outer diameter than the first row sun gear 111. The front end of the shaft 123 of the carrier that supports the pinion 122 that meshes with the sun gear 121 and ring gear 125 of the second row is connected to the ring gear 115 of the first row via the carrier connecting member 116, and the rear end of the shaft 123 is connected to the ring gear 115 of the first row. It is connected to a third row ring gear 135 via a connecting member 126 of another carrier.

Inner cylinder 800 integrated with third row sun gear 131
is connected to the inner race of the first one-way clutch 31 and the second one-way clutch 32, and is also connected to the clutch drum 830 of the third clutch 13. This clutch drum 830 also serves as a brake drum for the band-type second brake 22.

A carrier shaft 133 supporting the third row of pinions 132
is coupled to the output shaft 700 via the carrier coupling portion 136.

FIG. 1 is a sectional view showing a specific structure of the automatic transmission having the skeleton explained in FIG.

The starting device 2 that constitutes the automatic transmission 1 is a fluid transmission device, and includes a housing 200 that opens on the engine side (front side).
is housed inside. A carrier cover 204 is integrally attached to the rear of the front cover 202, which rotates in response to the engine's thrust.

A pump impeller 206 is mounted on the inner peripheral wall of the rear cover 204.
A turbine runner 208 is formed and disposed opposite the pump impeller 206 and is held by a turbine shell 210. The turbine shell 210 is connected at its inner peripheral portion to an input shaft 240 which is an output member of the starting device 2 and an input member of the transmission 3 via a connecting member 211 . A stator 214 is disposed between the pump impeller 206 and the turbine runner 208, and the inner peripheral portion of the stator 214 is connected to the outer race 215 of the one-way clutch 216, and the inner race 21 of the one-way clutch 216.
7 is attached to the outer periphery of the front end of the support tube 230. A lock-up clutch 220 having a lock-up piston 222 is disposed between the front force bar 202 and the turbine shell 210.

A cylindrical case 300 that houses the components of the transmission 3 is connected to the rear of the housing 200, and an oil pump cover 250 and a partition plate 270 are connected to the joint between the housing 200 and the transmission case 300. Attach the oil pump housing 260. An internal gear pump consisting of an external gear 262 and an internal gear 264 is accommodated within the oil pump housing 260, and the inner peripheral portion of the external gear 262 is connected to a shaft 266 that is integral with the carrier cover 204. The center portion of the oil pump cover 250 forms a cylindrical support portion 252 that protrudes rearward, and the rear outer circumference of the support tube 230 is press-fitted and fixed into the inner circumference of the support portion 252.

The support tube 230 supports the input shaft at two fulcrums on its inner circumference, and the rear end of the input shaft forms a radially expanding flange. The outer peripheral part of the flange part is the first clutch drum 40
The inner cylinder 410 is connected to the inner periphery of the rear end of the inner cylinder 410, which is integral with the inner cylinder 410. The first clutch 11 is housed inside the first clutch drum 400, and a piston 420 for operating the first clutch 11 is disposed.

The clutch plate 442 at the opposite end of the first clutch 11 from the piston 420 is extended rearward to form the clutch hub 44.
5, and a second clutch 12 and a piston 490 for operating the second clutch 12 are housed between the clutch hub 445 and a second clutch drum 470 disposed opposite to each other.

The inner peripheral portion of the rear end of the input shaft 240 supports the outer peripheral portion of the tip of the first intermediate shaft 500 via a bearing.

A radially expanding flange portion 510 is formed at the front portion of the first intermediate shaft 500, and a hub 520 of the first clutch 11
Connect to.

A drum 470a having a large width is integrally attached to the outer peripheral portion of the second clutch drum 470, and serves as a brake drum of the band-type first brake 21. The front end of the inner cylinder 480 of the clutch drum 470 is connected to the connecting member 61.
0 to the second intermediate shaft 600. The second intermediate shaft 600 has a cylindrical shape, and the outer peripheral portion of the first intermediate shaft 500 supports two fulcrums at the front and rear of its inner peripheral portion.

A central support member 3 is installed in the center of the transmission case 300.
Get 10. This central support member 310 is joined to the inner peripheral part of the transmission case at its outer peripheral part, and its central part is formed into a cylindrical part that protrudes forward. A ring member 320 is press-fitted into the outer circumferential portion of the cylindrical portion projecting forward, and the inner circumferential portion of the inner cylinder 480 of the second clutch drum 470 is rotatably supported by the outer circumferential portion of the ring member 320.

The intermediate shaft having a double structure extends rearward through the inner circumference of the central support member 310, and the outer circumference of the rear end of the first intermediate shaft 500 is supported by the inner circumference of the tip of the output shaft 700. A rear wall 330 is formed at the rear of the transmission case 300, and a rear support member 350 is fixed to the inner circumference of the rear wall 330.

The rear support member 350 includes a cylindrical portion that protrudes toward the front inside the transmission case 300, and the outer diameter of the cylindrical portion is formed into a plurality of stepped portions whose outer diameters gradually become smaller toward the front. . The inner peripheral portion of the front end of the cylindrical portion of the support member 350 is connected to the output shaft 7.
Supports the front outer circumference of 00.

A spigot engagement portion 360 is provided at the rear end of the transmission case 300.
The inner periphery of the rear end of the rear case 370, which is concentrically fitted through the rear case 370, supports the rear outer periphery of the output shaft 700 via a bearing. Therefore, the output shaft 700 is reliably supported by the two supporting points, and the first intermediate shaft 500 is reliably supported by the input shaft 240 and the output shaft 700 at its front and rear ends.

As explained in the skeleton of FIG. 2, three rows of simple planetary gear sets are arranged on the outer periphery of the connecting portion between the double-structured intermediate shafts 500, 600 and the output shaft 700. A first row of sun gears 111 is formed at the rear end of the second intermediate shaft 600 supported on the outermost side, and meshes with the pinion 112. The inner peripheral portion of the connecting member 114 is formed into a boss shape, and is rotatably held between the first and second intermediate shafts. A carrier support member 117 that supports the other end of the carrier shaft 113 is connected to the second row of ring gears 125 via a first connection member 150. The second row of ring gears 125 is further connected to the second ring gear via a second connecting member 160.
The one-way clutch 32 is connected to the outer race 810 of the one-way clutch 32. A multi-plate third brake 23 is disposed on the outer periphery of the first connecting member 150, and a piston 650 for operating the brake 23 is disposed on the rear wall of the central support member 310.

A second row of sun gears 121 is connected to the rear outer peripheral portion of the first intermediate shaft 500 . This second row of sun gear 121 is
It has a larger outer diameter than the sun gear 111 in the row. The front end of the shaft 123 of the carrier that supports the pinion 122 that meshes with the sun gear 121 and ring gear 125 of the second row is connected to the ring gear 115 of the first row through a connecting member 116 of the carrier.
The rear end of the shaft 123 is connected to a third row ring gear 135 via a connecting member 126 of another carrier.

The third row sun gear 131 has its rear end connected to the inner race 870 of the first one-way clutch 31 and also connected to the inner race 820 of the second one-way clutch 32 via the inner cylinder 800 . Inner cylinder 800
A third clutch 13 and a piston 880 for operating the third clutch 13 are housed inside the drum 830 formed opposite to the drum 830,
A clutch hub 815 is connected to the outer race 810 of the first one-way clutch 31. A band-type second brake 22 is disposed on the outer periphery of the clutch drum 830, and the clutch drum 830 also serves as a brake drum of the brake 22. Outer race 840 of second one-way clutch 32
The outer periphery of the transmission case 300 is fixed to the inner wall of the transmission case 300.

A carrier shaft 133 supporting the third row of pinions 132
is supported by a connecting portion 136 formed at the front end of the output shaft 700. A parking gear 710 and a speedometer drive gear 730 are attached to the outer periphery of the output shaft 700 inside the rear case 370, and a claw 720 that connects to the gear 710 is provided on the outside of the parking gear 710. . A connecting member 750 is attached to the rear end of the output shaft using a nut 7.
Fixed at 55.

Rotation sensors 305 and 3 for detecting the rotation speed of rotating members are installed in the main parts inside the transmission case 300 and rear case 370.
06, 307 to obtain information for controlling the frictional engagement elements.

A hydraulic control device (not shown) is attached to the bottom of the transmission case 300, and is controlled by a cover 309 that also serves as an oil pan.

As mentioned above, this automatic transmission is equipped with a 3-row simple planetary gear set.

Three clutches, three brakes as frictional engagement elements,
Two one-way clutches are used to achieve four forward speeds and one reverse speed, and the operation of each frictional engagement element will be described below.

Note that in the above table, the 0 mark indicates that the frictional engagement element is engaged, and the (0) mark indicates that it is engaged during engine braking.

Next, the power transmission system at each gear stage will be explained using FIGS. 3 to 7. The thick lines in the figure indicate power transmission lines, and the diagonal lines indicate fixed elements.

FIG. 3 shows the power transmission system at 1st speed, where the input from the input shaft 240 is transmitted from the clutch drum 400 to the first clutch 11, and via the first intermediate shaft 500 to the second row clutch 11. Simple planetary gear set sun gear 121
transmitted to. As a result, the carrier shaft 123 of the pinion 122 and the ring gear 125 both try to rotate. The second row ring gear 125 is connected to the outer race of the first one-way clutch 31 via a connecting member 160, and this rotation acts in the direction of engaging the first one-way clutch 31. The outer race and inner race of the first one-way clutch 31 are integrated. The third row sun gear 131 is integrally fixed to the inner periphery of the inner race.

This engagement connects the second row of ring gear 125 and the third row of sun gear 131. The third row sun gear 131 is integrally connected to an inner cylinder 800, and a second one-way clutch 32 is connected to the rear end of the inner cylinder 800.
An inner lace is formed. Therefore, the sun gear 131 of the third row, which is integrated with the ring gear 125 of the second row, tries to rotate the inner race of the second one-way clutch 32, but this rotation causes the second one-way clutch 32 to engage. act in the direction of Since the outer race of the second one-way clutch 32 engages with a fixed member such as a transmission case, the second one-way clutch 32 acts as a brake, and the second row of ring gear 125 and the third row of sun gear 131
supports the reaction force applied to the

As a result, the shaft 123 and the connecting member 126 that constitute the second row of carriers are driven at a reduced speed, and this power is transmitted to the third row of ring gear 135. The third row simple planetary gear set is the sun gear 131 as mentioned above.
is fixed, the shaft 133 and the connecting portion 136 constituting the carrier are driven at a reduced speed and transmitted to the output shaft 700.

In other words, the second row decelerates, and the third row decelerates, but the input of the first speed, where the transmitted torque is the largest, is transmitted through the second row sun gear, which has a large outer diameter, so the dimensions of the sun gear can be reduced. It doesn't need to be large.

When shifting from neutral gear to 1st gear, which is the lowest forward speed gear, a large amount of torque is transmitted to the drive path, but since two one-way clutches are inserted in series in the path that receives the reaction force, one-way clutches are inserted in series in the path that receives the reaction force. Shift shock can be absorbed by utilizing the characteristics of torsional rigidity when the clutch is engaged.

Fig. 4 shows the power transmission path when the vehicle is in 2nd speed, and is different from the state in 1st speed in that the sun gear 11.1 in the first row is fixed. In other words, shifting from 1st gear to 2nd gear is performed using the 1st gear.
The brake 21 of the second intermediate shaft 600 is engaged to fix the first row of sun gear 111 that is integral with the second intermediate shaft 600. This allows the first
The one-way clutch 31 is released, and the first row of carriers 1
13 and the second row ring gear 125 are also released. The third row, like the first speed, acts as a speed reducer that fixes the sun gear.

FIG. 5 shows the state of 3rd gear. To shift from 2nd gear to 3rd gear, release the first brake 21 and press the second clutch 1.
2 is transmitted from the first intermediate shaft 500 to the sun gear 121 of the second row, and from the second intermediate shaft 600 to the sun gear 111 of the first row, so that the first row and the second row are integrated. Rotate with. The third row, like the first and second speeds, acts as a speed reducer that fixes the sun gear.

FIG. 6 shows the power transmission path in 4th gear, but 4th gear is in a so-called direct connection state, and the planetary gear set does not rotate relative to each other. To shift from 3rd to 4th gear, the third clutch 13 is engaged. match. As a result, the carrier 113 in the first row, the ring gear 125 in the second row, and the sun gear 131 in the third row
is connected, and the second one-way clutch 32 is released.

The power of the input shaft 240 is transferred to the output shaft 70 without being subjected to speed change.
0.

FIG. 7 shows the power transmission path when moving in reverse. The second clutch 12 is engaged to transmit power to the first row sun gear 111 via the second intermediate shaft 600.

By engaging the third brake 23, the first row of carriers 113
Then, the third row sun gear 131 is fixed via the first and second connecting members 150° 160 and the first one-way clutch 31. Therefore, the power of the first row of ring gears 111 is decelerated and reversed and transmitted to the ring gear 115, and further decelerated in the third row and transmitted to the output shaft 700.

[Effects of the Invention] As described above, the present invention arranges three rows of simple planetary gear sets and frictional engagement elements in a concentrated manner, so that an automatic transmission with a compact axial dimension can be obtained. Input is selectively given to the sun gears of the first and second rows of the three-row simple planetary gear set, and the third row is used as a reduction gear, so the outer diameter dimension is It can be input to the large second row sun gear, and a gear train with reasonable strength can be constructed. In addition, since the sun gear, which receives the reaction force of the third row, which is a reduction gear, is connected to the fixed member via a one-way clutch, the mechanical shock absorption effect of the one-way clutch is used to shift from neutral to first gear. Shocks can be absorbed, and the one-way clutch also participates in shifting from 3rd to 4th gear, making it possible to achieve a smooth shift.

[Brief explanation of the drawing]

Fig. 1 is a sectional view of the automatic transmission of the present invention, Fig. 2 is an explanatory diagram showing the skeleton, Fig. 3 is an explanatory diagram showing the power transmission path in 1st gear, and Fig. 4 is an explanatory diagram showing the power transmission path in 2nd gear. An explanatory diagram showing the power transmission path. Fig. 5 is an explanatory diagram showing the power transmission path in 3rd speed. Fig. 6 is an explanatory diagram showing the power transmission path in 4th speed. Fig. 7 is an explanatory diagram showing the power transmission path in reverse. It is an explanatory view showing a power transmission path. 1... Automatic transmission. 2...Starting device, 3...Transmission, 11...First clutch, 12...Second clutch, 13... -Third clutch, 21...First brake, 22...Second brake, 23...Third brake. 31...First one-way clutch, 32...
...Second one-way clutch, 110...Simple planetary gear set in the first row, 120...Simple planetary gear set in the second row, 130...Simple planetary gear set in the third row.

Claims (1)

[Claims] (1) In an automatic transmission equipped with a starting device and a planetary gear device, between the three rows of simple planetary gear sets that are arranged together, and the input shaft that transmits the output of the starting device and the three rows of simple planetary gear sets. a first intermediate shaft that connects the first clutch and the sun gear of the second row simple planetary gear set; a first intermediate shaft that connects the first clutch and the sun gear of the first row simple planetary gear set; a second intermediate shaft disposed concentrically on the outer periphery of the first intermediate shaft that connects the sun gear of the gear set, and an output shaft that connects to the carrier of the simple planetary gear set of the third row; is connected to the ring gear of the second row and to the sun gear of the third row via the third clutch, the ring gear of the first row is connected to the carrier of the second row and the ring gear of the third row, and the ring gear of the first row is connected to the carrier of the second row and the ring gear of the third row. An automatic transmission characterized in that the sun gear is connected to a fixed part via a one-way clutch.