JP2003278853A - Automatic transmission for combined planetary gear type vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a transmission having preferably and possibly many forward speed change gears, in which the whole layout is very convenient and the whole structure is very compact, as the transmission for a vehicle comprising two planetary gears, two sets of a pair of gears, three clutches, and two brakes. <P>SOLUTION: A combined planetary gear is formed by connecting each part of forming components of two planetary gears. While a part of the forming components is selectively braked, rotation of an input member is input to the combined planetary gear selecting through two sets of a pair of the gear by means of selective connection of three clutches. Thus, the combined planetary gear is speed-changed by combination for a pair of the gear and the combined planetary gear. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automatic transmission for a vehicle, and more particularly, to an input member, an output member, two planetary gear units and two gear pairs provided between the input member, the output member and the planetary gear. A plurality of forward gear stages are provided by selectively connecting the components of the gear device and the gear pair directly or via the clutch, and selectively braking some of the components of the planetary gear device directly or via the gear pair. The present invention relates to an automatic transmission for a vehicle capable of achieving the above.

[0002]

2. Description of the Related Art Conventionally, two planetary gear devices are provided between an input member and an output member, and the input member, the output member, and the constituent elements of the planetary gear device are selectively connected to six clutches, and the planetary gear device is used. Japanese Unexamined Patent Publication (Kokai) No. 60-23658 discloses an automatic transmission for a vehicle that achieves 6 forward speeds and reverse speeds by selectively braking two brakes on some of the components of the apparatus. Further, in addition to incorporating the two planetary gear units together with the clutch and the brake between the input member and the output member as described above, it is also possible to incorporate a gear pair in order to provide a variety of gear ratios. It is disclosed in the official gazette.

[0003]

Two planetary gear units or further gear pairs are provided between an input member and an output member, and these input members, output members, planetary gear units, and components of the gear pairs are directly or clutched. It is possible to achieve a plurality of forward gears and at least one reverse gear by selectively braking the components of the planetary gear unit directly or through a pair of gears. There are endless possibilities to construct an automatic transmission for a vehicle. The present invention, under such infinite possibilities, requires as few clutches and brakes as possible and its arrangement is as convenient as possible, which allows for an overall configuration. An object of the present invention is to create a structure of a transmission that is as compact as possible and that can achieve more gear stages with a transmission ratio that is as preferable as possible for a vehicle transmission.

[0004]

As a first automatic transmission for a vehicle that solves the above-mentioned problems, the present invention provides an input member,
Single pinion type front side planetary gear unit having an output member, front side gear pair, rear side gear pair, sun gear, ring gear and carrier, and single pinion type rear side planetary gear unit having sun gear, ring gear and carrier A front side planetary gear unit and a rear side planetary gear unit, the front side sun gear is connected to the rear side sun gear, and the front side ring gear. Composes a compound planetary gear device by being coupled to the rear carrier, and the output member is arranged on the front side of the compound planetary gear device and coupled to the front carrier, and the output member is connected to the front and rear gear pairs and 1st and 2nd clutch are arrange | positioned at the rear side of a compound planetary gear device, and a front side and a rear side gear pair One gear of each is concentrically aligned with the first and second clutches and the compound planetary gear set, and the front gear pair is connected to the rear ring gear by one gear, and the first clutch Selectively connects one gear of the rear gear pair to the front sun gear and the rear sun gear, and the second clutch selectively couples one gear of the rear gear pair to the rear carrier and the front ring gear. And a third clutch is disposed laterally of the output member in concentric alignment with the other gears of the front gear pair and the rear gear pair, and the input member is connected to the front gear via the hollow shaft member. The other gear of the pair of rear gears is selectively coupled to the other gear of the pair, and the other gear of the pair of rear gears is coupled to the input member via the shaft member passing through the hollow shaft member, and the first brake is connected to the rear ring gear and the front gear. One tooth in a pair And the second brake selectively brakes the front side ring gear and the rear side carrier, and a combination of the selective coupling by each clutch and the selective braking by each brake. Therefore, we propose an automatic transmission for a vehicle, which is characterized by achieving 6 forward speeds.

However, in all the description including the claims of the present specification, the terms "front side" and "rear side" are simply referred to as between the constituent members along the axial direction of the automatic transmission. The relative front-rear relationship is displayed, and does not show the correspondence to the front part and the rear part of the vehicle when the automatic transmission is mounted on the vehicle. Further, in the description of the embodiments of the first to fourth vehicle automatic transmissions according to the present invention given below with reference to the drawings, the reverse gear obtained by the embodiment will be explained at the same time as the forward gear. However, the automatic transmission for vehicles proposed by the present invention does not necessarily include the reverse gear. Particularly in vehicles such as automobiles in recent years, it has been attempted to use an electric motor as a part of the vehicle drive in various modes regardless of whether it is a so-called hybrid vehicle or not. It is possible to

As a second automatic transmission for a vehicle for solving the above problems, the present invention has an input member, an output member, a front gear pair, a rear gear pair, a sun gear, a ring gear and a carrier. A double pinion type front planetary gear device, a single pinion type rear planetary gear device having a sun gear, a ring gear and a carrier; first to third clutches; and first and second brakes, The front side planetary gear unit and the rear side planetary gear unit form a compound planetary gear unit by connecting the front side ring gear with the rear side ring gear and the front side carrier with the rear side carrier, and the output member is It is arranged on the front side of the compound planetary gear unit and is connected to the front ring gear and the rear ring gear,
The front and rear gear pairs and the first and second clutches are arranged on the rear side of the compound planetary gear device, and one of the front and rear gear pairs has the first gear.
And the second clutch and the compound planetary gear set are concentrically aligned, the front gear pair is connected to the rear carrier and the front carrier by one gear, and the first clutch is the rear gear pair. One gear is selectively connected to the front sun gear, the second clutch is selectively connected to one gear of the rear gear pair to the rear sun gear, and the third clutch is connected to the side of the output member. Arranged concentrically with the other gear of each of the front gear pair and the rear gear pair, and selectively connecting the input member to the other gear of the front gear pair via the hollow shaft member, and the rear gear The other gear of the pair is coupled to the input member via a shaft member passing through the hollow shaft member, the first brake selectively brakes the rear sun gear, and the second brake of the other of the front gear pair. Selectively brake gears It has become so, proposes a vehicular automatic transmission, characterized in that it is configured to achieve a 6-forward-by the combination of selective braking by the respective brake selectively connected by the clutches.

In the above-mentioned second automatic vehicle transmission,
The compound planetary gear device may be configured as a Ravigneaux type planetary gear device in which the front side ring gear and the rear side ring gear are integrated and the front side carrier and the rear side carrier are integrated.

As a third automatic transmission for a vehicle which solves the above problems, the present invention has an input member, an output member, a front gear pair, a rear gear pair, a sun gear, a ring gear and a carrier. A single-pinion type front planetary gear device, a single-pinion type rear planetary gear device having a sun gear, a ring gear and a carrier; first to third clutches; and first and second brakes, The front side planetary gear unit and the rear side planetary gear unit form a compound planetary gear unit by connecting the front side sun gear with the rear side sun gear and the front side carrier with the rear side ring gear, and the output member is It is arranged on the front side of the compound planetary gear unit and is connected to the front carrier and the rear ring gear. The gear pair and the first and second clutches are arranged on the rear side of the compound planetary gear device, and one gear of each of the front and rear gear pairs is provided with the first and second clutches and the compound planetary gear device. Are concentrically aligned with each other, the front gear pair is connected to the rear carrier by one gear, and the first clutch selectively connects one gear of the rear gear pair to the front ring gear, Two
Of the rear side gear pair selectively connects one gear of the rear side gear pair to the rear side sun gear and the front side sun gear, and a third clutch laterally of the output member of each of the front side gear pair and the rear side gear pair. The input gear is concentrically aligned with the other gear and selectively connects the input member to the other gear of the front gear pair via the hollow shaft member, and the other gear of the rear gear pair moves through the hollow shaft member. The first brake is selectively braked on the rear sun gear and the front sun gear, and the second brake is selectively braked on the other gear of the front gear pair by being coupled to the input member via the passing shaft member. Thus, an automatic transmission for a vehicle is proposed, which is configured to achieve 6 forward speeds by a combination of selective connection by each clutch and selective braking by each brake.

As a fourth automatic transmission for a vehicle which solves the above-mentioned problems, the present invention has an input member, an output member, a front gear pair, a rear gear pair, a sun gear, a ring gear and a carrier. A single-pinion type front planetary gear device, a single-pinion type rear planetary gear device having a sun gear, a ring gear and a carrier; first to third clutches; and first and second brakes, The front side planetary gear unit and the rear side planetary gear unit form a compound planetary gear unit by connecting the front side carrier with the rear side ring gear and the front side ring gear with the rear side carrier, and the output member is It is arranged on the front side of the compound planetary gear unit and is connected to the front carrier and the rear ring gear. The side gear pair and the first and second clutches are arranged on the rear side of the compound planetary gear device, and one gear of each of the front and rear gear pairs is provided with the first and second clutches and the compound planetary gear device. And the front gear pair are connected to the rear carrier and the front ring gear by one gear, and the first clutch selects one gear of the rear gear pair as the front sun gear. And the second clutch selectively connects one gear of the rear gear pair to the rear sun gear, and the third clutch laterally connects the front gear pair and the rear gear pair to the side of the output member. Each of the other gears is concentrically aligned and arranged, and the input member is selectively connected to the other gear of the front gear pair via the hollow shaft member, and the other gear of the rear gear pair is connected to the hollow gear member. A shaft member that passes through Is connected to the input member through the first brake selectively braking the front sun gear being adapted to a second brake selectively braking the front ring gear and the rear-side carrier,
An automatic transmission for a vehicle is proposed, which is configured to achieve six forward speeds by a combination of selective connection by each clutch and selective braking by each brake.

In any of the above-described first to fourth vehicle automatic transmissions, the first and second clutches may be arranged on the rear side of the rear gear pair.

Furthermore, in any of the above-mentioned first to fourth vehicle automatic transmissions, the output member may directly drive the differential device.

The first automatic transmission for a vehicle is basically of a single pinion type having an input member, an output member, first and second gear pairs, a sun gear, a ring gear and a carrier. It has first and second planetary gear units, first to third clutches, and first and second brakes, and the first and second planetary gear units are connected with sun gears, and The ring gear is connected to the latter carrier to form a compound planetary gear device, and the output member is connected to the carrier of the first planetary gear device, and one gear of each of the first and second gear pairs. Are concentrically aligned with the first and second clutches and the compound planetary gear set, the first gear pair being connected at one gear to the ring gear of the second planetary gear set, the first clutch being the second One of a pair of gears Cars selectively connected to the sun gear of the first and second planetary gear device, the second clutch is a second
Selectively couple one of the gears of the first gear pair to the carrier of the second planetary gear set and the ring gear of the first planetary gear set, and the third clutch connects the input member to the other gear of the first gear set. And the other gear of the second gear pair is coupled to the input member, and the first brake selectively couples the ring gear of the second planetary gear set and one gear of the first gear pair. The second brake selectively brakes the ring gear of the first planetary gear device and the carrier of the second planetary gear device, and selectively connects the clutches and the brakes. 6 forward gears may be achieved by a combination of selective braking according to.

[0013]

According to the above respective configurations, two planetary gear devices, two gear pairs, three clutches,
By using the two brakes, it is possible to achieve the forward gears having the preferable gear ratios as the six types of vehicle transmissions.

In particular, as will be better understood from the following description of the embodiments, the front and rear gear pairs are arranged on the rear side of the compound planetary gear device, and the third clutch is of the compound planetary gear device. It is arranged on the front side and on the side of the output member arranged there, and is concentrically aligned with the other gears of the front gear pair and the rear gear pair, and the input member is the third clutch and the hollow shaft. A member selectively coupled to the other gear of the front gear pair beyond the compound planetary gear device, and an input member coupled to the other gear of the rear gear pair by a shaft member passing through the hollow shaft member,
When the input to the compound planetary gear device is selectively changed from the rear side to two types and the output is taken out from the front side of the compound planetary gear device, even if the output member is a gear, The three clutches can be arranged laterally next to each other, reducing the axial length of the automatic transmission.

Furthermore, when the first and second clutches are arranged on the rear side of the rear gear pair, the first and second clutches are located on the front side where the driving force is taken in and out of the automatic transmission. Since these clutches are arranged at the farthest end on the rear side, these clutches have excellent proximity and maintenance thereof is easy. Thus, the flexibility of the arrangement of the clutch and the brake is increased, and the structure of the entire transmission is made compact.

[0016]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of each of the first to fourth automatic transmissions will be described below in detail with reference to the accompanying drawings.

FIG. 1A attached is a schematic view showing the construction of one embodiment of the first automatic transmission for a vehicle. In the figure, IN indicates an input member and OUT indicates an output member. Pf and Pr are planetary gear units, respectively.
f and Gr are gear pairs, respectively. In the description of the present application, the planetary gear device closer to the input member is referred to as a front planetary gear device or front side Pf, and the planetary gear device farther from the input member is referred to as a rear planetary gear device or rear side Pr. To call. Then, for each of the front side Pf and the rear side Pr, the sun gear, the ring gear, and the carrier are indicated as Sf, Rf, Cf and Sr, Rr, Cr, respectively, and the front side sun gear, the front side ring gear, the front side carrier and the rear side sun gear, respectively. Rear side ring gear and rear side carrier. Also, the gear pair Gf
And Gr, the gear pair Gf on the side closer to the input member
Is referred to as a front gear pair, and the gear pair Gr farther from the input member is referred to as a rear gear pair. In the case of FIG. 1, both Pf and Pr are single pinion type planetary gear devices, the front side Pf and the rear side sun gears are connected to each other, and the front side Pf ring gear is the rear side Pr.
The compound planetary gear device is configured by being connected to the carrier.

The input member IN is rotatably supported by a bearing device (not shown) for rotation about an axis of rotation. The input member IN is connected by a shaft member Si to a gear g1 which is one of the gears of the rear gear pair Gr, and a gear g2 meshing with the gear g1 is connected to one rotating member of the clutches C1 and C2. The other rotating member of the clutch C1 is connected to the respective sun gears on the rear side Pr and the front side Pf. The input member IN is also connected to a gear g3, which is one of the gears of the front gear pair Gf, via a clutch C3 and a hollow shaft member So surrounding the shaft member Si, and the gear g4 meshing with the gear g3 is a rear side Pr. It is connected to the ring gear.

The ring gear on the rear side Pr is selectively braked by the brake B1, and the ring gear on the front side Pf and the carrier on the rear side Pr connected thereto are selectively braked by the brake B2. .
The output member OUT is connected to the carrier on the front side Pf. In this embodiment, the output member OUT is configured as a gear, and the pinion carrying frame F of the differential device Df is formed by a gear g5 directly meshing with the output member OUT.
p is driven, and a pair of left and right axles Sl and Sr are driven via a well-known differential gear mechanism shown in the figure. According to the above-mentioned structure, the engine side-mounted FF vehicle is conveniently constructed by coaxially connecting the crankshaft of the engine to the front side of the input member IN.
This also applies to the other embodiments described below.

The first automatic transmission for a vehicle according to the present invention shown as an embodiment in FIG. 1 is basically a clutch C1 to C3, brakes B1 and B2, a gear pair Gf.
The positions of Gr and Gr are not limited to the illustrated arrangement. For example, the clutch C3 may be arranged on the rear side of the compound planetary gear device instead of being arranged on the front side of the compound planetary gear device as shown in the drawing. In that case,
Further, the clutch C3 may be arranged on either the front side or the rear side of the gear pair Gf and Gr. Clutch C
When 3 is arranged on the rear side of the gear pair Gf and Gr, the gear g1 of the gear pair Gr is directly connected to the input member IN via the hollow shaft and the housing of the clutch C3, and the gear g3 of the gear pair Gf is so arranged. It may be connected to the clutch C3 by means of a shaft passed through a hollow shaft. Furthermore, the clutch C3 may be arranged at a position between the gear pair Gf and Gr, in which case the input member and the gear g1 are directly connected on the one hand and the clutch is on the other hand without using a hollow shaft. The input member and the gear g3 can be connected via C3.
The gear pair Gr may also be arranged on the rear side of the clutches C1 and C2, which provides a large space for arranging the clutch C3 between the gear pair Gf and Gr.

The transmission mechanism constructed as shown in FIG. 1A has a clutch C1, C2, C3 and a brake B1, B.
2 is engaged or released by the combination shown in the table of FIG. 1B, the six forward speeds of the first speed to the sixth speed (1st to 6th) and one of the forward speeds shown in the same table. Reverse gear (R) can be achieved. In the table, ○ indicates engagement and × indicates release. As can be understood from the table, the number of clutches or brakes engaged at each shift speed is two, and at any forward shift speed, switching to the adjacent forward shift speed is By disengaging only one of them and engaging the other clutch or brake. The front side Pf and the rear side Pf
The ratio of the number of teeth of the sun gear to the number of teeth of the ring gear in each of r is represented by ρf and ρr. As an example, ρf = 0.41, ρr = 0.49, and the front gear pair Gf and The reduction ratios of the rear gear pair Gr are represented by δf and δr, respectively.
When f = 2.52 and δr = 1.00, the gear ratios (reduction ratios) at each gear are as shown in the table. The gear ratio width between the first speed and the sixth speed is 5.49.

The gear ratio at each gear can be obtained from the alignment chart as shown in C of FIG. The principle of the alignment chart is as follows.

First, the relative relationship of the rotation angle (and therefore also the rotation speed) among the sun gear, the ring gear and the carrier in one planetary gear device is determined by parallelizing the coordinate lines representing the respective rotation angles (or rotation speeds). It can be obtained by intersecting a straight line with the coordinate system arranged in. in this case,
When the planetary gear device is a single pinion type, the parallel coordinate lines are arranged such that the coordinate line of the ring gear and the coordinate line of the sun gear are arranged in parallel on both sides of the carrier coordinate line with the number of teeth of the ring gear set. Is ρ (ρ <1), the ratio of the distance from the carrier coordinate line to the ring gear coordinate line and the distance from the carrier coordinate line to the sun gear coordinate line is ρ to 1.

When the planetary gear device is a double pinion type, the parallel coordinate lines are arranged such that the ring gear coordinate line and the sun gear coordinate line are located on the same side with respect to the carrier coordinate line, and the ring gear coordinate line with respect to the carrier coordinate line. The ratio of the distance separating the lines and the distance separating the sun gear coordinate line from the carrier coordinate line is ρ to 1.

Therefore, as shown in FIG. 1A, the front side Pf and the rear side Pr are both single pinion type planetary gear devices, and the former sun gear is connected to the latter sun gear. As for the case where the ring gear is connected to the latter carrier, the front side sun gear Sf and the rear side sun gear Sr act together as one body, and at the same time, the front side ring gear Rf and the rear side carrier C.
Since r and R have to act together, Sf and Sr are combined in the Sf-Cf-Rf coordinate system for the front side Pf and the Sr-Cr-Rr coordinate system for the rear side Pr. In addition, Rf and Cr must match. This means that, as viewed in FIG. 1C, the Sf-Cf-Rf coordinate system for the front side Pf and the Sr-Cr-Rr coordinate for the rear side Pr must be considered in combination as shown.

Based on the above recognition, the gear ratio (reduction ratio) of each gear is obtained from the collinear chart as follows.
In the collinear diagram, at each point on the straight line B1-B2, the rotation speed of the rotary member braked by the engagement of the brakes B1 and B2 is 0, and at each point on the straight line C1-C2. ,
The sun gears on the front side Pf and the rear side Pr, or the carrier on the rear side Pr and the ring gear on the front side Pf, which are connected to the input member by the engagement of the clutches C1 and C2, change the rotational speed of the input member to the reduction ratio of the rear gear pair Gr. Rotate at the number of revolutions decelerated by and pass through point C3
At each point on a straight line parallel to, the rear-side Pr ring gear connected to the input member by the engagement of the clutch C3 has a rotational speed reduced by the speed reduction ratio of the front-side gear pair Gf. It shall rotate. The collinear chart illustrated in C of FIG. 1 is drawn so as to show the procedure for obtaining the gear ratio of each shift stage as clearly as possible, and ρf = 0 that yields the gear ratio illustrated in B of FIG. .41, ρr = 0.
49, δf = 2.52, δr = 1.00 are not drawn. This also applies to each of FIGS. 2 to 4 below.

First, regarding the first speed, the clutch C1 and the brake B2 are engaged at this time. The rotation speed of the front ring gear Rf is 0 due to the engagement of the brake B2. On the other hand, the engagement of the clutch C1 causes the front sun gear Sf to rotate at a rotation speed obtained by reducing the input rotation speed by the reduction ratio of the rear gear pair. Therefore,
Sf, Cf, and Rf on the front side Pf are all straight lines C1-
Cf on 1-B2 and connected to the output member OUT rotates at the speed of point 1. When expressed as a reduction ratio, the gear ratio of the first gear is a value obtained by dividing the distance between the straight line B1-B2 and the straight line C1-C2 by the distance of the point 1 with respect to the straight line B1-B2. It is obtained as a value multiplied by the reduction ratio of.

At the second speed, clutch C1 and brake B
1 and 1 are engaged. The engagement of the clutch C1 causes the rear sun gear Sr to rotate at a rotational speed that is the input rotational speed reduced by the reduction ratio of the rear gear pair. The rear ring gear Rr is stopped by the engagement of the brake B1. Therefore, Sr, Cr, and Rr on the rear side Pr are all straight lines C1-2-a-B.
1, the front ring gear Rf connected to the rear carrier Cr rotates at the rotational speed of the point a. Therefore, Sf, Cf, and Rf on the front side Pf are all on the straight line C1-2-a, and the front side Cf connected to the output member OUT rotates at the rotational speed of point 2. The procedure for calculating the gear ratio as the reduction gear ratio is the same as that for the first speed stage.

At the third speed, the clutches C1 and C3 are engaged. When the clutch C1 is engaged, the sun gear on the rear side Pr rotates at a rotational speed that is the rotational speed of the input member reduced by the gear pair Gr, and when the clutch C3 is engaged, the rear side is rotated. In Pr, the ring gear rotates at the rotational speed that is the rotational speed of the input member reduced by the gear pair Gf. Therefore, in the alignment chart, S
The value of r is at point C1 and the value of Rr is at point C3, so the value of Cr is at point b along the straight line C1-b-C3.
On the front side Pf, the sun gear is on the rear side Pr.
The sun gear rotates with the sun gear and the ring gear rotates with the carrier on the rear side Pr. Therefore, Sf is a point C in the alignment chart.
1 and Rf is at point b, so the carrier and the output member connected to it rotate at the rotational speed of point 3 on the straight line C1-3-b. The procedure for calculating the gear ratio as the reduction gear ratio is the same as that for the first speed stage.

At the fourth speed, the clutches C1 and C2 are engaged. Since the former sun gear Sf and the latter sun gear Sr are connected to each other on the front side Pf and the rear side Pr, the former ring gear Rf and the latter carrier Cr are connected to each other by engagement of the clutches C1 and C2. Then, Pf and Pr are both locked, and the two planetary gear devices simply rotate as an integral rotating body. The rotational speed of the integral rotation of the two planetary gear units is the rotational speed of the input member, and the rear side gear pair Gr.
It is the rotation speed decelerated by. In the examples shown in the table, the reduction ratio δr of Gr is 1.00, so the gear ratio is 1.00.

At the fifth speed, the clutches C2 and C3 are engaged. By engaging the clutch C2, the carrier on the rear side Pr rotates at a rotational speed that is the rotational speed of the input member reduced by the rear gear pair Gr, and the clutch C3 engages. The ring gear on the rear side Pr rotates at the rotational speed reduced by the front side gear pair Gf. Therefore, in the alignment chart, Cr is at point C2, Rr is at point C3, and Sr
Is at the point c on the extension of the straight line connecting the points C2 and C3, and the rear side Pr acts along the straight line c-C2-C3. Therefore, on the front side Pf, Sf is at the point c, Rf is at the point C2, and the carrier and the output member connected thereto rotate at the rotational speed of the point 5 on the straight line c-5-C2. The procedure for calculating the gear ratio as the reduction gear ratio is the same as that for the first speed stage. In this case, the shift stage is an overdrive stage depending on the reduction ratio of the rear gear pair Gr.

At the sixth speed, clutch C2 and brake B
1 is engaged. On the rear side Pr by the engagement of the clutch C2 and the brake B1, the carrier rotates at the rotational speed reduced by the rear side gear pair Gr, and the rotation of the ring gear is braked to 0. Therefore, Sr is at the point d on the extension of the straight line connecting the points B1 and C2 in the alignment chart. Therefore, at the front side Pf, Sf
Is at point d and Rf is at point C2, so that its carrier and the output member connected to it are straight lines d-6-C2.
It rotates at the rotation speed of point 6 above. The procedure for calculating the gear ratio as the reduction gear ratio is the same as that for the first speed stage. Also in this case, the shift stage is an overdrive stage depending on the reduction ratio of the front gear pair Gr.

At the reverse gear R, the clutch C3 and the brake B2 are engaged. Clutch C3 and brake B2
When and are engaged, in the rear side Pr, the ring gear is rotated at a speed obtained by reducing the rotational speed of the input member by the front side gear pair Gf while the carrier is fixed. Therefore, Cr is at point B2 and Rr is at point C3 in the alignment chart.
Sr is at point e on the extension of points C3 and B2. Therefore, at this time, in the front side Pf, S
f, Cf, and Rf act along the straight line e-R-B2, respectively, and the carrier and the output member connected thereto are at the point R.
Rotates at a negative rotation speed of, that is, reverses. The procedure for calculating the gear ratio as the reduction gear ratio is the same as that for the first speed stage.

FIGS. 2A, 2B and 2C are views similar to FIGS. 1A, 1B and 1C showing one embodiment of the second automatic vehicle transmission. In the figure, IN, OUT, Pf, Pr, G
Definitions of f, Gr, and others are the same as those in FIG.
In this case, Pf is a double pinion type planetary gear device and Pr is a single pinion type planetary gear device,
Both of these ring gears are integrated, and a planetary pinion on the front side Pf and a planetary pinion on the rear side Pr that mesh with the ring gears are integrated, and by combining both carriers, a Ravigneaux type planetary gear device is configured. Has been done.

A front side Pf, a rear side Pr, and a front side gear pair G between the input member IN and the output member OUT.
The connection of f, the rear gear pair Gr, the clutches C1 to C3, and the brakes B1 and B2 is as shown in A of FIG. 2, and each speed stage is achieved by the combination of engagement and disengagement of these clutches and brakes. The outline is as shown in B of FIG. Also in this table, ○ indicates engagement and × indicates release. As can be understood from the table, the number of clutches or brakes engaged at each shift speed is two, and at any forward shift speed, switching to the adjacent forward shift speed is By disengaging only one of them and engaging the other clutch or brake. Further, as an example, the ratios ρf and ρr of the number of teeth of the sun gear to the number of teeth of the ring gear on the front side Pf and the rear side Pr are respectively ρf = 0.37 and ρr =
0.45 and the reduction ratios δf and δr of the front gear pair Gf and the rear gear pair Gr are δf = 1.
When 00 and δr = 1.53, the gear ratio at each shift speed is as shown in the table, and the gear ratio width between the first speed and the sixth speed is 6.04.

As shown in FIG. 2A, the front side Pf, which is a double pinion type planetary gear device, and the rear side Pr, which is a single pinion type planetary gear device, are connected to the former ring gear Rf and the latter ring gear Rr. Since the former carrier Cf and the latter carrier Cr are connected, the front side ring gear Rf and the rear side ring gear Rr.
And at the same time, the front carrier Cf and the rear carrier Cr act together,
Therefore, in the superposition of the Sf-Rf-Cf coordinate system for the front side Pf and the Rr-Cr-Sr coordinate system for the rear side Pr, Rf and Rr match and Cf and Cr match.

Based on the above recognition, the gear ratio (reduction ratio) of each gear is obtained from the alignment chart shown in C of FIG. Based on the combination of the coordinate system of the front side Pf and the coordinate system of the rear side Pr, the output member OU in each shift stage
The point for determining the points 1, 2, 3, 4, 5, 6, and R indicating the rotation speed of T is clear from the above description with reference to FIG. 1, and therefore a further detailed description of this point will be given. , Omitted to avoid making the specification redundant.

FIGS. 3A, 3B and 3C are views similar to FIGS. 1A, 1B and 1C showing one embodiment of the third vehicle automatic transmission. In the figure, IN, OUT, Pf, Pr, G
Definitions of f, Gr, and others are the same as those in FIG.
In this case, both Pf and Pr are single pinion type planetary gear devices.

A front side Pf, a rear side Pr, and a front side gear pair G between the input member IN and the output member OUT.
f, the rear gear pair Gr, the clutches C1 to C3, and the brakes B1 and B2 are connected as shown in A of FIG. 3, and each speed stage is achieved by a combination of engagement and disengagement of these clutches and brakes. The outline is as shown in B of FIG. Also in this table, ○ indicates engagement and × indicates release. As can be understood from the table, the number of clutches or brakes engaged at each shift speed is two, and at any forward shift speed, switching to the adjacent forward shift speed is By disengaging only one of them and engaging the other clutch or brake. Further, as an example, the ratios ρf and ρr of the number of teeth of the sun gear to the number of teeth of the ring gear on each of the front side Pf and the rear side Pr are ρf = 0.54 and ρr =
0.45 and the reduction ratios δf and δr of the front gear pair Gf and the rear gear pair Gr are δf = 1.
When 00 and δr = 1.53, the gear ratio at each shift speed is as shown in the table, and the gear ratio width between the first speed and the sixth speed is 6.04.

As shown in FIG. 3A, in the front side Pf and the rear side Pr, the former sun gear Sf is the latter sun gear S.
Since the former carrier Cf is connected to the latter ring gear Rr, the front-side sun gear Sf and the rear-side sun gear Sr act together as a unit, and at the same time, the front-side carrier Cf and the rear-side ring gear Rr are connected. Act as one, and Rf about front side Pf
-Cf-Sf coordinate system and Rr-Cr for rear Pr
The superposition of the -Sr coordinate system is such that Sf and Sr match and Cf and Rr match.

Based on the above recognition, the gear ratio (reduction ratio) of each gear is obtained from the alignment chart as shown in C of FIG. Based on the combination of the coordinate system of the front side Pf and the coordinate system of the rear side Pr, the output member OU in each shift stage
The point for determining the points 1, 2, 3, 4, 5, 6, and R indicating the rotation speed of T is clear from the above description with reference to FIG. 1, and therefore a further detailed description of this point will be given. , Omitted to avoid making the specification redundant.

FIGS. 4A, 4B and 4C are views similar to FIGS. 1A, 1B and 1C showing one embodiment of the fourth automatic vehicle transmission. In the figure, IN, OUT, Pf, Pr, G
Definitions of f, Gr, and others are the same as those in FIG.
In this case, both Pf and Pr are single pinion type planetary gear devices.

A front side Pf, a rear side Pr, and a front side gear pair G between the input member IN and the output member OUT.
The connection of f, the rear gear pair Gr, the clutches C1 to C3, and the brakes B1 and B2 is as shown in A of FIG. 4, and each speed stage is achieved by the combination of engagement and disengagement of these clutches and brakes. The outline is as shown in B of FIG. Also in this table, ○ indicates engagement and × indicates release. As can be understood from the table, the number of clutches or brakes engaged at each shift speed is two, and at any forward shift speed, switching to the adjacent forward shift speed is By disengaging only one of them and engaging the other clutch or brake. As an example, the ratios ρf and ρr of the number of teeth of the sun gear to the number of teeth of the ring gear on the front side Pf and the rear side Pr are respectively ρf = 0.58 and ρr =
0.45 and the reduction ratios δf and δr of the front gear pair Gf and the rear gear pair Gr are δf = 1.
When 00 and δr = 1.53, the gear ratio at each shift speed is as shown in the table, and the gear ratio width between the first speed and the sixth speed is 6.04.

As shown in FIG. 4A, in the front side Pf and the rear side Pr, the former carrier Cf is connected to the latter ring gear Rr, and the former ring gear Rf is connected to the latter carrier Cr. Front carrier Cf
And the rear side ring gear Rr act together as a unit, and at the same time, the front side ring gear Rf and the rear side carrier Cr.
And act together, S about front side Pf
f-Cf-Rf coordinate system and Rr-C for rear Pr
When the r-Sr coordinate systems are superposed, Cf and Rr match and Rf and Cr match.

Based on the above recognition, the gear ratio (reduction ratio) of each gear is obtained from the alignment chart as shown in C of FIG. Based on the combination of the coordinate system of the front side Pf and the coordinate system of the rear side Pr, the output member OU in each shift stage
The point for determining the points 1, 2, 3, 4, 5, 6, and R indicating the rotation speed of T is clear from the above description with reference to FIG. 1, and therefore a further detailed description of this point will be given. , Omitted to avoid making the specification redundant.

Although the present invention has been described in detail above with respect to four embodiments, it will be apparent to those skilled in the art that various modifications can be made to these embodiments within the scope of the present invention. .

[Brief description of drawings]

FIG. 1 is a schematic diagram of a transmission mechanism showing a first embodiment of an automatic transmission for a vehicle according to the present invention (A), a list of engagement / disengagement combinations of clutches and brakes (B), and gear ratios. Alignment chart (C).

FIG. 2 is a schematic view of a speed change mechanism showing a second embodiment of an automatic transmission for a vehicle according to the present invention (A), a list of engagement / disengagement combinations of clutches and brakes (B), and a gear ratio is obtained. Alignment chart (C).

FIG. 3 is a schematic view of a speed change mechanism showing a third embodiment of an automatic transmission for a vehicle according to the present invention (A), a list of engagement / disengagement combinations of a clutch and a brake (B), and a gear ratio. Alignment chart (C).

FIG. 4 is a schematic view of a speed change mechanism showing a fourth embodiment of an automatic transmission for a vehicle according to the present invention (A), a list of engagement / disengagement combinations of clutches and brakes (B), and a gear ratio. Alignment chart (C).

[Explanation of symbols]

Pf, Pr ... Planetary gear device Gf, Gr ... Gear pair IN: Input member OUT ... Output member C1-C3 ... Clutch B1-B2 ... Brake Df ... Differential device

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Hiroshi Fujito             1 Toyota Town, Toyota City, Aichi Prefecture Toyota Auto             Car Co., Ltd. (72) Inventor Shigekazu Yugo             1 Toyota Town, Toyota City, Aichi Prefecture Toyota Auto             Car Co., Ltd. F term (reference) 3J028 EA08 EB08 EB13 EB31 EB37                       EB62 EB66 FA06 FB05 FC13                       FC16 FC17 FC23 FC24 FC63                       GA01

Claims (8)

[Claims] 1. An input member, an output member, a front gear pair, a rear gear pair, a single pinion type front planetary gear unit having a sun gear, a ring gear and a carrier, and a sun gear, a ring gear and a carrier. Single pinion type rear side planetary gear device,
A third clutch and first and second brakes are provided, and in the front planetary gear unit and the rear planetary gear unit, the front sun gear is connected to the rear sun gear, and the front ring gear is the rear carrier. The composite planetary gear device is configured by being connected, and the output member is arranged on the front side of the composite planetary gear device and connected to the front carrier, and the front and rear gear pairs and the first and second A clutch and a clutch are arranged on the rear side of the compound planetary gear device, and one gear of each of the front-side and rear-side gear pairs is the first gear.
And the second clutch and the compound planetary gear device are concentrically aligned, the front gear pair is connected to the rear ring gear by one gear, and the first clutch connects one gear of the rear gear pair. By selectively connecting the front sun gear and the rear sun gear,
Of the rear side gear pair selectively connects one gear of the rear side gear pair to the rear side carrier and the front side ring gear, and a third clutch laterally of the output member of each of the front side gear pair and the rear side gear pair. The input gear is concentrically aligned with the other gear and selectively connects the input member to the other gear of the front gear pair via the hollow shaft member, and the other gear of the rear gear pair is inserted through the hollow shaft member. The first brake selectively couples the rear ring gear and one gear of the front gear pair, and the second brake couples the front ring gear and the rear carrier. For a vehicle, which is configured to selectively brake, and is configured to achieve six forward stages by a combination of selective connection by each clutch and selective braking by each brake. Dynamic transmission. 2. An input member, an output member, a front gear pair, a rear gear pair, a double pinion type front planetary gear unit having a sun gear, a ring gear and a carrier, and a sun gear, a ring gear and a carrier. A rear side planetary gear device of a single pinion type, first to third clutches, and first and second brakes,
The front side planetary gear unit and the rear side planetary gear unit form a compound planetary gear unit by connecting the front side ring gear with the rear side ring gear and the front side carrier with the rear side carrier, and the output member is The front side of the compound planetary gear device is connected to the front ring gear and the rear ring gear, and the front and rear gear pairs and the first and second clutches are arranged on the rear side of the compound planetary gear device. , One gear of each of the front and rear gear pairs is the first
And the second clutch and the compound planetary gear device are concentrically aligned with each other, the front gear pair is connected to the rear carrier and the front carrier by one gear, and the first clutch is the rear gear pair. One gear is selectively connected to the front sun gear, the second clutch is selectively connected to one gear of the rear gear pair to the rear sun gear, and the third clutch is connected to the side of the output member. Arranged concentrically with the other gears of the front gear pair and the rear gear pair, and selectively connecting the input member to the other gear of the front gear pair via the hollow shaft member, and the rear gear The other gear of the pair is connected to the input member via a shaft member passing through the hollow shaft member, the first brake selectively brakes the rear sun gear, and the second brake of the other of the front gear pair. Selectively control gears Has become so doing, vehicular automatic transmission, characterized in that it is configured to achieve a 6-forward-by the combination of selective braking by the respective brake selectively connected by the clutches. 3. The compound planetary gear device is configured as a Ravigneaux type planetary gear device in which a front side ring gear and a rear side ring gear are integrated and a front side carrier and a rear side carrier are integrated. Claim 2
The automatic transmission for vehicles described in. 4. An input member, an output member, a front gear pair, a rear gear pair, a single pinion type front planetary gear unit having a sun gear, a ring gear and a carrier, and a sun gear, a ring gear and a carrier. Single pinion type rear side planetary gear device,
A third clutch and first and second brakes are provided. In the front planetary gear unit and the rear planetary gear unit, the front sun gear is connected to the rear sun gear, and the front carrier is the rear ring gear. The output member is arranged on the front side of the composite planetary gear device and is connected to the front carrier and the rear ring gear, and is connected to the front and rear gear pairs and the first and second gear pairs. A first clutch and a second clutch are arranged on the rear side of the compound planetary gear device, and one gear of each of the front-side and rear-side gear pairs is the first gear.
And the second clutch and the compound planetary gear set are concentrically aligned, the front gear pair is connected to the rear carrier by one gear, and the first clutch connects one gear of the rear gear pair. The second clutch selectively connects to the front ring gear, the second clutch selectively connects one gear of the rear gear pair to the rear sun gear and the front sun gear, and the third clutch extends to the side of the output member. Arranged concentrically with the other gears of the front gear pair and the rear gear pair, and selectively connecting the input member to the other gear of the front gear pair via the hollow shaft member, and the rear gear The other gear of the pair is coupled to the input member via a shaft member that passes through the hollow shaft member, the first brake selectively brakes the rear sun gear and the front sun gear, and the second brake is the front brake. Gear pair A vehicle that is configured to selectively brake the other gear, and is configured to achieve six forward speeds by a combination of selective connection by each clutch and selective braking by each brake. Automatic transmission for. 5. An input member, an output member, a front gear pair, a rear gear pair, a single pinion type front planetary gear unit having a sun gear, a ring gear and a carrier, and a sun gear, a ring gear and a carrier. Single pinion type rear side planetary gear device,
A third clutch and first and second brakes are provided, and in the front planetary gear unit and the rear planetary gear unit, the front carrier is connected to the rear ring gear and the front ring gear is the rear carrier. The output member is arranged on the front side of the composite planetary gear device and is connected to the front carrier and the rear ring gear, and is connected to the front and rear gear pairs and the first and second gear pairs. A first clutch and a second clutch are arranged on the rear side of the compound planetary gear device, and one gear of each of the front-side and rear-side gear pairs is the first gear.
And the second clutch and the compound planetary gear device are concentrically aligned with each other, the front gear pair is connected to the rear carrier and the front ring gear by one gear, and the first clutch is the rear gear pair. One gear is selectively connected to the front sun gear, the second clutch is selectively connected to one gear of the rear gear pair to the rear sun gear, and the third clutch is connected to the side of the output member. Arranged concentrically with the other gears of the front gear pair and the rear gear pair, and selectively connecting the input member to the other gear of the front gear pair via the hollow shaft member, and the rear gear The other gear of the pair is connected to the input member via a shaft member that passes through the hollow shaft member, the first brake selectively brakes the front sun gear, and the second brake the front ring gear and the rear carrier. Is selectively braked, and is configured to achieve 6 forward speeds by a combination of selective coupling by each clutch and selective braking by each brake. transmission. 6. The first and second clutches are arranged on the rear side with respect to the rear side gear pair.
5. The automatic transmission for vehicles according to any one of 5 to 5. 7. The output member is adapted to directly drive the differential device.
The automatic transmission for vehicles according to any one of 6 above. 8. An input member, an output member, and first and second members.
The first and second planetary gear units of single pinion type having a pair of gears, a sun gear, a ring gear, and a carrier, first to third clutches, and first and second brakes. The sun gears of the second planetary gear unit are connected to each other, and the former ring gear is connected to the latter carrier to form a compound planetary gear unit. The output member is connected to the carrier of the first planetary gear unit. And one gear of each of the first and second gear pairs is a first gear.
And concentrically aligned with the second clutch and the compound planetary gear set, the first gear pair being connected at one gear to the ring gear of the second planetary gear set, and the first clutch being the second gear pair. One gear is selectively coupled to the sun gears of the first and second planetary gear sets, and a second clutch connects one gear of the second gear pair to the carrier of the second planetary gear set and the first gear of the second planetary gear set. A third clutch selectively connects the input member to the other gear of the first gear pair and a second gear of the second gear pair connects to the input member. And a first brake selectively braking the ring gear of the second planetary gear set and one gear of the first gear pair, and the second brake and the ring gear of the first planetary gear set and the second gear. It is designed to selectively brake the carrier of the planetary gear system. , Automatic transmission vehicle, characterized in that it is configured to achieve selective coupling to the 6-forward-by a combination of selective braking by the brake by the clutches.