JPH08254251A - Planetary gear row for automatic transmission and gear transmission for automatic transmission - Google Patents

Abstract

PURPOSE: To provide a planetary gear row for automatic transmission and a gear transmission for automatic transmission which can reduce speed change shock easily, facilitate speed change control, excel in power performance, and have a simple configuration. CONSTITUTION: A planetary gear row for automatic transmission and a gear transmission for automatic transmission are provided with a first two-element connection member d which connects a first planetary gear a of single pinion type, a second planetary gear b of single pinion type, a third planetary gear c of single pinion type, a first sun gear, and a second sun gear integrally, a second two-element connection member g which connects a clutch interposition connecting member f which connects a first carrier and a third ring gear through a connection and disconnection clutch e, a first ring gear, and a second carrier integrally, and a third two-element connection member h which connects a second ring gear and a third carrier integrally.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear transmission for an automatic transmission.

[0002]

2. Description of the Related Art Conventionally, as a gear transmission for an automatic transmission which obtains a forward five speed gear, a gear transmission disclosed in JP-A-1-242854 is known.

In this conventional device, one single-pinion type planetary gear is added to a four-speed type main planetary gear shifting mechanism that obtains a forward four-speed gear stage by using two single-pinion type planetary gears. It consists of a planetary gear and a total of 11 clutches, brakes, one-way clutches, and other engagement / disengagement elements.

Of these, a one-way clutch for simplifying the shift control and a clutch without the clutches and brakes added for the purpose of applying the engine brake, which has no one-way clutch when the coasting is applied, are provided. The number of engagement / release elements of the brake is seven. This number is practically the minimum number of elements required to achieve a shift of 5 forward gears and 1 reverse gear.

The breakdown is a four-step portion (two underdrive steps, one direct connection step, one overdrive step) that requires at least five engagement / release elements for the clutch and brake, and one planetary gear and clutch. It consists of an add-on section that requires at least two brakes, enabling five speeds (three underdrives, one direct connection, one overdrive).

[0006]

However, when trying to change the overdrive from one stage to two stages in the above-described conventional gear transmission for an automatic transmission, the input path of the add-on section is switched to change the add-on section. Can lead to
For this purpose, it is necessary to add two clutches and brakes. Therefore, it is not practical in consideration of the cost and the point of impairing the vehicle mountability.

The minimum number of clutch and brake transmission elements required for the add-on type five-speed transmission is seven, but the weight and size of the entire apparatus are large.
There is also a strong demand to reduce this as much as possible to improve cost, vehicle mountability, fuel efficiency, etc.

In order to reduce the total number of clutches and brakes, the structure of the transmission is considered by combining a plurality of planetary gears. The method of combining the planetary gears and the ratio of the number of teeth of the sun gear to the ring gear of the planetary gears are considered. (That is,
Gear ratio), whether the single pinion type planetary gear or double pinion type planetary gear is used, etc., the obtained gear ratio changes variously, and not all of them can be put to practical use. However, practical gear trains are limited by various conditions such as required power performance and cost.

That is, although a huge number of configurations can be devised depending on the combination of the planetary gears and the setting method of the gear ratio, it is very difficult to create a practically required one as an automatic transmission for a vehicle. There is a problem with.

For example, Japanese Unexamined Patent Publication No. 50-64660 uses three single-pinion type planetary gears, three clutches, and three brakes, as shown in FIG.
As shown in FIG. 5, there is shown a device that achieves 6 forward gears and 2 reverse gears by engaging and disengaging each element.

However, in this conventional device,
There are the problems described below.

(1) The setting of the gear ratio between gears is inappropriate.

The axis of abscissas is the position of the rotary member that is assigned according to the set gear ratio of the planetary gears, and the axis of ordinates is the rotation speed ratio. The rotation speed ratio is 0 and the rotation speed ratio 1 corresponds to the horizontal direction. FIG. 14 shows a collinear diagram in which elements of the clutch and the brake are displayed at the intersections with the drawn straight line and the lines connecting the engaged elements are drawn.

Originally, it is desirable to set the gear ratio between the gear stages in a geometric progression. Because, as shown in FIG.
The torque band of the engine (the width of the engine torque output from the relationship between the engine torque and the rotation at a constant throttle opening) is almost constant without being affected by the gear stage, and the output shaft torque is almost constant according to the gear stage. As the engine speed changes with the ratio, the engine speed changes almost the same, which makes the driver feel comfortable.

However, according to FIG. 14, the gear ratios between the gear stages are not in a geometric series, and particularly, between the fifth speed, the sixth speed, and the third speed.
The range between the 4th speed and the 4th speed is wide, and a torque band different from other shifts is used during this period, so that a portion having good engine characteristics cannot be used. In particular, the fifth and sixth speeds are places where the shift frequency is high, and should be noticeable.

Therefore, if the gear ratio of the planetary gears is set so that the vertical axis of the fifth rotating member shifts to the right in the drawing in an attempt to narrow the third speed and the fourth speed, the third speed and the fourth speed become narrow but at the same time. It will be narrowed between the 4th and 5th speeds, and will be wider than the current speed between the 5th and 6th speeds.

As described above, in the gear train in which the power transmission paths of the gears are always connected, the selection range of the gear ratio is small, and the gear ratio must be compromised as shown in FIG.

(2) The member rotation that is not involved in gear shifting becomes abnormally high.

The rotating members at the left and right ends of the alignment chart shown in FIG. 14 have abnormally high rotation speeds in the fifth speed, the sixth speed, and the second reverse speed. There is a risk of gear shifting failure (clutch operation failure due to centrifugal oil pressure, etc.).

The present invention overcomes the above-mentioned problems and creates one suitable for practical use. In this regard, the following points were taken into consideration.

1) When the two clutches and brakes are switched from the engaged state to the released state or from the released state to the engaged state, the gear shift shock becomes worse, or complicated control is required to reduce the gear shift shock. Consider,
One clutch or brake is switched from the engaged state to the released state or from the released state to the engaged state between the adjacent gears.

2) In order to simplify the structure and suppress the cost increase, the double pinion type planetary gears are not used, and only three single pinion type planetary gears are combined.

3) The total number of clutches and brakes is 6 in the minimum case, and it is possible to realize 6 forward stages (3 underdrive stages, 1 direct connection stage, 2 overdrive stages) and 1 or more reverse stages. did. This is because a compact and lightweight structure and cost reduction were strongly considered.

4) Since the add-on type has a structure in which the add-on part is connected to the main body part, in consideration of the small size, light weight and cost, the means for connecting the add-on part, the main body part and the add-on part are combined. It is disadvantageous in that it requires a wall to separate the two.
Therefore, we decided to use the integral type.

5) The gear ratios between the respective gears are arranged in a geometric progression so as to reduce variations in engine rotation before and after gear shifting and to facilitate driving.

The object of the present invention is to easily reduce the shift shock, control the shift easily, have excellent power performance, and have a simple structure. The planetary gear train for automatic transmission and the gear shift for automatic transmission. To provide a device.

[0027]

In order to achieve the above object, in the planetary gear train for an automatic transmission according to claim 1, a first sun gear, a first ring gear, and Single pinion type first planetary gear a having a first carrier that holds a pinion meshing with both gears
A second sun gear, a second ring gear, and a single pinion type second planetary gear b having a second carrier that holds a pinion meshing with both gears, a third sun gear, and a third sun gear.
A ring gear, a third planetary gear c of a single pinion type having a third carrier that holds a pinion that meshes with both gears, and a first two-element connecting member d that integrally connects the first sun gear and the second sun gear. , A clutch interposition connecting member f for connecting the first carrier and the third ring gear via a connecting / disconnecting clutch e, the first ring gear and the second ring
A second two-element connecting member g for integrally connecting with the carrier
And a third two-element connecting member h that integrally connects the second ring gear and the third carrier.

According to a second aspect of the present invention, in the automatic transmission planetary gear train of the first aspect, the first two-element connecting member d is connected to the input shaft via a second clutch. And the clutch interposition connecting member f.
The third ring gear side of is connected to the output shaft, and the second
The element connecting member g is connected to the case via the first brake, and is connected to the input shaft via the third clutch,
The third two-element connecting member h is connected to the case via a second brake, the third sun gear is connected to the case via a third brake, and one gear stage is connected to the connecting / disconnecting clutch e ( A shift control means is provided that obtains a combination of three engagements among three clutches and three brakes including a first clutch) and obtains a plurality of gears according to an engagement release control rule that does not cause double replacement in adjacent gears. It is characterized by that.

According to a third aspect of the present invention, in the automatic transmission planetary gear train of the first aspect, the first two-element connecting member d is directly connected to the input shaft, and the clutch is provided. The third ring gear side of the interposed connecting member f is connected to the output shaft, and the second two-element connecting member g is connected.
Is connected to the case via the first brake, is connected to the input shaft via the third clutch, and the third two-element connecting member h is connected to the case via the second brake. The three sun gears are connected to the case via the third brake, and one gear stage is obtained by an engagement combination of two out of two clutches and three brakes including the connecting / disconnecting clutch e (first clutch), and adjacent to each other. It is characterized in that a shift control means is provided for obtaining a plurality of gears according to an engagement release control rule which does not cause double shifts in the gears.

[0030]

The operation of the first invention will be described.

Of the single-pinion type first planetary gear a, second planetary gear b, and third planetary gear c, the first sun gear and the second sun gear are integrally connected by the first two-element connecting member d, The first ring gear and the second carrier are the second 2
The second ring gear and the third carrier are integrally connected by the element connecting member g, and are integrally connected by the third two-element connecting member h. The two elements of the first carrier and the third ring gear are integrally connected when the connection / disconnection clutch e is selected, and the two elements are separated when the connection / disconnection clutch e is selected.

That is, of the nine rotating elements of each planetary gear a, b, c, three two-element connecting members d, g, h reduce the number by three. Then, when the connection / disconnection clutch e is selected to be disengaged, a planetary gear train having 9-3 = 6 rotating elements is provided, and when the connection / disconnection clutch e is selected to be connected, a two-element connecting member is further added. By doing, 9
It becomes a planetary gear train having 3-1 = 5 rotating elements.

Therefore, an input member, an output member, and a case are added to these rotary elements to form 9 or 8 members, and the members are integrally connected or not connected at all, or the members such as clutches and brakes are connected. It is possible to obtain a rotation state with different gear ratios between the input member and the output member by controlling the engagement / disengagement of a plurality of provided engagement elements by performing either one of the coupling through the coupling element. .

In this case, the power transmission paths of the planetary gears a, b, and c can be selected by disconnecting or connecting the connecting / disconnecting clutch e, so that the degree of freedom in setting the gear ratio at each gear is increased, and each gear can be changed. It is possible to arrange the gear ratios between the stages in a geometric progression.

Further, by using the connection / disconnection clutch e to disconnect the transmission path, it is possible to prevent the member rotation not involved in gear shifting from becoming abnormally high.

The operation of the second invention will be described.

With respect to the gear speed change mechanism according to the second aspect of the present invention, by the speed change control by the speed change control means, three engagement combinations of three clutches and three brakes in which one gear stage includes a disconnecting clutch e (first clutch). And a plurality of gears can be obtained by the engagement release control law without double replacement in the adjacent gears.

For example, when 6 forward gears and 1 reverse gear are set from a plurality of gears that can be set, the shift shock can be easily reduced, the shift control is easy, the power performance is excellent, and the structure is simple. Satisfies all required performance.

The operation of the third invention will be described.

In the gear shift mechanism according to the third aspect of the present invention, by the shift control by the shift control means, two engagement combinations of two clutches and three brakes, one gear stage of which includes the engagement / disengagement clutch e (first clutch). And a plurality of gears can be obtained by the engagement release control law without double replacement in the adjacent gears.

For example, when 5 forward gears and 1 reverse gear are set from a plurality of gears that can be set, gear shift shock can be easily reduced, gear shift control is easy, power performance is excellent, and the structure is simple. Satisfies all required performance.

[0042]

Embodiments of the present invention will be described below with reference to the drawings.

First, the structure will be described.

FIG. 2 is a skeleton diagram showing a gear shifting mechanism for an automatic transmission according to an embodiment corresponding to the first and second aspects of the invention.

In FIG. 2, PG1 is the first planetary gear, P
G2 is the second planetary gear, PG3 is the third planetary gear, M1 is the first two-element connecting member, M2 is the clutch interposition connecting member, M3 is the second two-element connecting member, and M4 is the third two-element connecting member. The member C1 is the first clutch (corresponding to the connecting / disconnecting clutch e), and the planetary gear train composed of these members will be described.

The first planetary gear PG1 is a single pinion type planetary gear having a first sun gear S1, a first ring gear R1, and a first carrier P1 holding a pinion meshing with both gears S1 and R1.

The second planetary gear PG2 is a single pinion type planetary gear having a second sun gear S2, a second ring gear R2, and a second carrier P2 holding a pinion meshing with both gears S2 and R2.

The third planetary gear PG3 is a single pinion type planetary gear having a third sun gear S3, a third ring gear R3, and a third carrier P3 holding a pinion meshing with both gears S3, R3.

The first two-element connecting member M1 is the first
It is a member that integrally connects the sun gear S1 and the second sun gear S2.

The clutch intervening connecting member M2 has a first
The carrier P1 and the third ring gear R3 are connected to the first clutch C.
It is a member connected through 1.

The second two-element connecting member M3 has a first
It is a member that integrally connects the ring gear R1 and the second carrier P2.

The third two-element connecting member M4 has a second
It is a member that integrally connects the ring gear R2 and the third carrier P3.

Members and engagement elements added to the planetary gear train when the above planetary gear train is used as a gear shift mechanism for an automatic transmission will be described.

The first two-element connecting member M1 (rotating member A) is connected to the input shaft IS via the second clutch C2.

The third ring gear R3 side of the clutch intervening connecting member M2 (rotating member B) is connected to the output shaft OS.

The second two-element connecting member M3 (rotating member C) is connected to the case K via the first brake B1 and the input shaft I via the third clutch C3.
It is connected to S.

The third two-element connecting member M4 (rotating member D) is connected to the case K via the second brake B2.

The third sun gear S3 (rotating member E)
Is connected to the case K via the third brake B3.

One gear is provided for the three clutches C1, C2, C3 and the three brakes B1, B2, B3.
Out of the gear shift control means (total hydraulic control) Type or electronic control + hydraulic control type) is connected to the gear transmission mechanism for the automatic transmission.

Next, the operation will be described.

[First Speed Gear Stage] The first speed gear stage is obtained by engaging the first clutch C1, the second clutch C2 and the first brake B1 as shown in the engagement logic table of FIG. To be

At this first speed, the first clutch C1
The rotation member B integrally rotates as a two-element connection member due to the engagement. The input from the rotating member A is provided by the engagement of the second clutch C2. The rotary member C is fixed to the case K by the engagement of the first brake B1.

Therefore, the rotation of the rotating member B is regulated by the input from the rotating member A and the fixing of the rotating member C, and from the output shaft OS connected to the rotating member B,
The first speed gear ratio can be obtained by the underdrive having a large reduction ratio with respect to the rotation of the input shaft IS.

That is, the collinear diagram at the first speed gear stage is represented by one diagram by the engagement of the first clutch C1 as shown at 1st in FIG.

In FIG. 3, A, B, C, D, and E are rotating members, and arrows indicate inputs, double circles indicate outputs, and black triangles indicate brake engagement.

[Second Speed Gear Stage] The second speed gear position is the second brake position B when the first brake B1 in the first speed gear position is released.
Conclude 2. That is, as shown in the engagement logic table of FIG. 4, it is obtained by engaging the first clutch C1, the second clutch C2, and the second brake B2.

In this second gear, the first clutch C1
The rotation member B integrally rotates as a two-element connection member due to the engagement. Further, the input from the rotating member A is caused by the engagement of the second clutch C2. And the second brake B2
The rotation member D is fixed to the case K by the engagement.

Therefore, the rotation of the rotating member B is defined by the input from the rotating member A and the fixing of the rotating member D, and from the output shaft OS connected to the rotating member B,
It is possible to obtain the second speed gear ratio that is smaller than the first speed gear ratio as the reduction ratio.

That is, the collinear chart at the second speed gear stage is represented by one chart by engagement of the first clutch C1 as shown at 2nd in FIG.

[Third Speed Gear] In the third speed, the third brake B is released by releasing the second brake B2 in the second speed.
Conclude 3. That is, as shown in the engagement logic table of FIG. 4, it is obtained by engaging the first clutch C1, the second clutch C2, and the third brake B3.

In this third gear, the first clutch C1
The rotation member B integrally rotates as a two-element connection member due to the engagement. Further, the input from the rotating member A is caused by the engagement of the second clutch C2. And the third brake B3
The rotation member E is fixed to the case K by the engagement.

Therefore, the rotation of the rotating member B is defined by the input from the rotating member A and the fixing of the rotating member E, and from the output shaft OS connected to the rotating member B,
It is possible to obtain the third speed gear ratio that is a value that is smaller than the second speed gear ratio.

That is, the collinear diagram at the third speed gear stage is represented by one diagram by engagement of the first clutch C1, as indicated by 3rd in FIG.

[Fourth gear] In the fourth gear, the third brake B3 in the third gear is released to release the third clutch C.
Conclude 3. That is, as shown in the engagement logic table of FIG. 4, it is obtained by engaging the first clutch C1, the second clutch C2, and the third clutch C3.

At this fourth speed, the first clutch C1
The rotation member B integrally rotates as a two-element connection member due to the engagement. Further, the input from the rotary member A due to the engagement of the second clutch C2 and the input from the rotary member C due to the engagement of the third clutch C3 are simultaneous inputs.

Therefore, the rotation of the rotary member B is defined as the input rotation by the simultaneous input from the rotary members A and C, and the output shaft OS connected to the rotary member B
The fourth speed gear ratio based on the gear ratio 1 is obtained.

That is, the collinear chart at the fourth speed gear stage is represented by one chart by engagement of the first clutch C1 as shown at 4th in FIG.

[Fifth speed gear stage] The fifth speed gear stage releases the second clutch C2 in the fourth speed gear stage to release the third brake B.
Conclude 3. That is, as shown in the engagement logic table of FIG. 4, it can be obtained by engaging the first clutch C1, the third clutch C3, and the third brake B3.

At this fifth speed, the first clutch C1
The rotation member B integrally rotates as a two-element connection member due to the engagement. Further, the input from the rotating member C is provided by the engagement of the third clutch C3. And the third brake B3
The rotation member E is fixed to the case K by the engagement.

Therefore, the rotation of the rotating member B is regulated by the input from the rotating member C and the fixing of the rotating member E, and from the output shaft OS connected to the rotating member B,
The fifth speed gear ratio is obtained by the overdrive gear ratio of higher rotation than the input shaft IS.

That is, the collinear chart at the fifth gear is represented by one chart by engagement of the first clutch C1 as shown at 5th in FIG.

[Sixth speed gear stage] In the sixth speed gear position, the first clutch C1 in the fifth speed gear position is released to release the second clutch C.
Conclude 2. That is, as shown in the engagement logic table of FIG. 4, it is obtained by engaging the second clutch C2, the third clutch C3, and the third brake B3.

At this sixth speed, the first clutch C1
Is released, the third ring gear R3 side of the rotating member B and the first carrier P1 side are separated. Further, the input from the rotary member A due to the engagement of the second clutch C2 and the input from the rotary member C due to the engagement of the third clutch C3 are simultaneous inputs. The rotating member E is fixed to the case K by the engagement of the third brake B3.

Therefore, by the input from the rotating member D accompanying the input rotation of the rotating members A and C and the fixing of the rotating member E, the rotation of the rotating member B on the side of the third ring gear R3 is regulated, and the rotation of the rotating member B becomes the first rotation. From the output shaft OS connected to the side of the 3-ring gear R3, the sixth speed gear ratio based on the overdrive gear ratio of higher rotation than the input shaft IS is obtained.

That is, the collinear chart at the sixth gear is represented by two charts by releasing the first clutch C1 as shown at 6th in FIG.

[Reverse Gear Stage] The reverse gear stage is obtained by engaging the second clutch C2, the first brake B1 and the third brake B3 as shown in the engagement logic table of FIG.

In this reverse gear, the release of the first clutch C1 causes the rotation member B to move toward the first ring gear R3 side and the first ring gear R3 side.
It is separated from the carrier P1 side. Also, the second clutch C
By the engagement of 2, the input is from the rotating member A. The rotating members C and E are fixed to the case K by the engagement of the first brake B1 and the third brake B3.

Therefore, the third ring gear R3 of the rotating member B is fixed by rotating the rotating member D, which is defined by the input of the rotating member A and fixing the rotating member B, and fixing the rotating member E.
Side rotation is regulated, and the third ring gear R of the rotating member B is defined.
From the output shaft OS connected to the third side, a reverse gear speed change ratio can be obtained by reverse rotation with respect to the input shaft IS.

That is, the alignment chart at the reverse gear is shown in FIG.
As shown in Rev of No. 2 by releasing the first clutch C1
It is represented by two diagrams.

[Gear Ratio] Gear ratio ρ ₁ (= z _S1 / z _R1 ) of the first planetary gear PG1, gear ratio ρ ₂ (= z _S2 / z _R2 ) of the second planetary gear PG2, third When the gear ratio ρ ₃ (= z _S3 / z _R3 ) of the planetary gear PG3 is set, each gear speed ratio n
1, n2, n4, n5, n6 and nR are as shown in the table of FIG.

As a specific example, ρ ₁ = 0.400, ρ ₂ =
When 0.350 and ρ ₃ = 0.660, the gear ratio of each gear and the ratio between adjacent gears are as follows. The target value is shown in parentheses.

N1 = 3.500 (3.5) n2 / n1 = 0.607 (0.629) n2 = 2.124 (2.2) n3 / n2 = 0.681 (0.682) n3 = 1 .447 (1.5) n4 / n3 = 0.691 (0.667) n4 = 1.000 (1.0) n5 / n4 = 0.820 (0.700) n5 = 0.820 (0.7 ) N6 / n5 = 0.734 (0.714) n6 = 0.602 (0.5) nR = 1.721 The gear ratios of the first speed to the sixth speed are almost the target speed ratios. Further, the ratio between the 1st speed and the 6th speed is within the range of allowable deviation from the target ratio.

[First Modification] FIGS. 5 and 6 are nomographic diagrams and an engagement logic table showing the first modification. The first modification corresponds to the examples shown in FIGS. On the other hand, only the engagement rule at the sixth gear is different.

In the sixth speed gear of the first modification, the third brake B3 in the fifth speed gear is released and the second brake B2 is engaged. That is, as shown in the engagement logic table of FIG. 6, the first clutch C1, the third clutch C3, and the second brake B2.
It is obtained by engaging. At the sixth speed, the rotating member B integrally rotates as a two-element connecting member due to the engagement of the first clutch C1. Further, the input from the rotating member C is provided by the engagement of the third clutch C3. The rotating member D is fixed to the case K by the engagement of the second brake B2.

Therefore, the rotation of the rotating member B is regulated by the input from the rotating member C and the fixing of the rotating member D, and from the output shaft OS connected to the rotating member B,
The sixth speed gear ratio is obtained by the overdrive gear ratio of higher rotation than the input shaft IS. By the way, n6 = 0.550.

That is, the collinear chart at the sixth gear is represented by one chart by engagement of the first clutch C1 as shown at 6th in FIG.

[Second Modification] A second modification of the embodiment corresponding to the invention described in claims 1 and 3 will be described.

FIG. 7 is a skeleton diagram showing a second modified example of the embodiment, and FIG. 8 is a diagram showing an engagement logic table in the shift control in the second modified example.

In this second modified example, the second clutch C2 is eliminated and the first two-element connecting member M1 (rotating member A) is directly connected to the input shaft IS in contrast to the example shown in FIGS. As shown in FIG. 7) and FIG. 8, one gear has two clutches 3
This is an example in which two forward gears are obtained by combining the two engagements of the brakes, and the adjacent forward gears are controlled by the engagement release control rule without double replacement.

In this second modification, as is clear from the comparison between FIG. 4 and FIG. 8, the sixth speed gear stage in FIG. 4 is changed to the fifth speed gear stage in FIG. The fifth clutch is achieved by eliminating the second clutch C2 without changing the shift control law.

[Third Modification] The third modification shown in the skeleton diagrams of FIGS. 9 and 10 is different from the embodiment shown in FIG. 2 in that the third planetary gears PG are sequentially arranged from the input side toward the output side.
In this example, the third planetary gear PG2 and the first planetary gear PG1 are arranged. Note that FIG. 9 shows an example in which 6 forward gears are achieved by 3 clutches and 3 brakes, and FIG. 10 shows an example in which 5 forward gears are achieved by two clutches 3 brakes in which the second clutch C2 is eliminated.

[Fourth Modification] The fourth modification shown in the skeleton diagrams of FIGS. 11 and 12 is different from the embodiment shown in FIG.
From the input side to the output side, the first planetary gears PG are sequentially
In this example, the first, third planetary gears PG3, and second planetary gears PG2 are arranged. Note that FIG. 11 shows an example of achieving 6 forward speeds with 3 clutches 3 brakes, and FIG. 12 shows an example of achieving 5 forward speeds with 2 clutches 3 brakes in which the second clutch C2 is eliminated.

Next, the effect will be described.

The gear transmission for an automatic transmission according to the embodiment also achieves the following advantages.

(1) Since the gear shift to the adjacent gear is performed by releasing one engagement element and engaging one engagement element, the shift shock can be easily reduced.

(2) The number of engaging elements required for shifting is 3 even though it is a device for performing shifting control of 6 forward gears and 1 reverse gear.
Since only six clutches and three brakes are used, the shift control becomes easy.

(3) Since the gear ratio of each gear is close to the target gear ratio and the gear ratios of the adjacent gears are arranged in a substantially geometric progression, the engine rotation changes during gear shifting. Changes almost in the same manner, and gear shifting is achieved in a torque band with good engine characteristics without being affected by the gear ratio, resulting in excellent power performance.

Here, the reason why the gear ratio of each gear can be made close to the target gear ratio and the ratio of the gears between the adjacent gears can be arranged in a substantially geometric progression is explained. To be more specific, the power transmission paths of the three planetary gears are not always fixed, and the power transmission path can be selected by engaging / disengaging the first clutch C1, so that the first clutch C1 is released. And a collinear diagram when the first clutch C1 is in the engaged state (one diagram) are separately drawn, and a gear ratio at each gear position is shown. The degree of freedom in setting is greatly increased.

(4) Only three single pinion type planetary gears are used, the type is an integral type instead of the add-on type, and the number of engaging elements required for shifting is three clutches and three. Since the device has only 6 brakes,
The configuration is simple, and it is possible to achieve small size, light weight, and low cost.

(5) As the 6th forward speed shift control law, the second 6th forward speed shift control law is changed because the second clutch C2 is released only in one gear (5th speed or 6th speed). Instead, by eliminating the second clutch C2, it is possible to easily achieve five forward gears.

Although the embodiments have been described above with reference to the drawings, the specific configuration is not limited to the embodiments, and modifications and additions within the scope of the present invention are included in the present invention. Be done.

For example, a gear transmission mechanism having the planetary gear train for an automatic transmission according to claim 1 is included in the present invention.

Further, in the embodiment, the example of the gear shifting mechanism for the automatic transmission using only the engaging elements necessary for shifting is shown, but in order to simplify the control, the one-way clutch is put in, or the one-way clutch is used. Even if you put a clutch, add braking means so that the engine braking works on the coasting side,
Furthermore, it goes without saying that the elements connecting the input shaft and the output shaft and the elements to be fixed to the case may be appropriately determined as necessary.

[0114]

According to the planetary gear train for automatic transmissions of the first aspect, the first planetary gear of single pinion type, the second planetary gear of single pinion type, and the third planetary gear of single pinion type. A first two-element connecting member that integrally connects the first sun gear and the second sun gear, and a clutch interposition connecting member that connects the first carrier and the third ring gear via a disconnecting clutch. Since the configuration includes the second two-element connecting member that integrally connects the ring gear and the second carrier and the third two-element connecting member that integrally connects the second ring gear and the third carrier, the shift shock It is possible to provide an effect that it is possible to provide a planetary gear train for an automatic transmission, in which the gear ratio can be easily reduced, the gear shift control is easy, the power performance is excellent, and the configuration is simple.

According to a second aspect of the present invention, in the automatic transmission planetary gear train of the first aspect, the first two-element coupling member is input through the second clutch. While connecting to the shaft, the third ring gear side of the clutch intervening connecting member is connected to the output shaft, and the second two-element connecting member is connected to the case via the first brake.
A third clutch connected to the input shaft via a third clutch, a third two-element connecting member connected to the case via a second brake, and a third sun gear connected to the case via a third brake;
One gear is obtained by an engagement combination of three out of three clutches and three brakes including the connection / disconnection clutch (first clutch), and a plurality of gears are provided at adjacent gears according to an engagement release control rule without double replacement. To provide a gear transmission for an automatic transmission, which is capable of easily reducing shift shock, has easy shift control, is excellent in power performance, and has a simple structure because it is a device provided with a shift control means for obtaining the gear stage of The effect of being able to do is obtained.

In the automatic transmission gear transmission according to the third aspect, in the automatic transmission planetary gear train according to the first aspect, the first two-element connecting member is directly connected to the input shaft,
The third ring gear side of the clutch intervening connecting member is connected to the output shaft, the second two-element connecting member is connected to the case via the first brake, and is connected to the input shaft via the third clutch. , The third two-element connecting member is connected to the case via the second brake, the third sun gear is connected to the case via the third brake, and one gear stage is connected to the connecting / disconnecting clutch (the first clutch). A device provided with a shift control means for obtaining a plurality of gear stages according to an engagement release control rule which does not cause double replacement in adjacent gear stages and which is obtained by an engagement combination of two of the two clutches and three brakes including Therefore, it is possible to provide an effect that a gear shift shock can be easily reduced, gear shift control is easy, power performance is excellent, and a gear transmission for an automatic transmission having a simple configuration can be provided.

[Brief description of drawings]

FIG. 1 is a claim correspondence diagram showing a planetary gear train for an automatic transmission according to the present invention.

FIG. 2 is a skeleton diagram showing a gear transmission mechanism for an automatic transmission of the embodiment apparatus.

FIG. 3 is a collinear chart showing a member rotating state at each gear in the gear shift control in the embodiment apparatus.

FIG. 4 is a diagram showing an engagement logic table at each gear in the shift control in the embodiment apparatus.

FIG. 5 is a collinear chart showing a member rotating state at each gear in the shift control of the first modified example of the embodiment apparatus.

FIG. 6 is a diagram showing an engagement logic table at each gear in the shift control in the first modified example of the embodiment apparatus.

FIG. 7 is a skeleton diagram showing a gear shift mechanism for an automatic transmission according to a second modified example of the embodiment apparatus.

FIG. 8 is a diagram showing an engagement logic table at each gear in the shift control of the second modified example of the embodiment apparatus.

FIG. 9 is a third example of the example apparatus with three clutches and three brakes
It is a skeleton diagram showing a gear shift mechanism for an automatic transmission of a modified example.

FIG. 10 is a skeleton diagram showing a gear shift mechanism for an automatic transmission according to a third modified example using the two clutches and three brakes of the embodiment apparatus.

FIG. 11 is a skeleton diagram showing a gear shift mechanism for an automatic transmission according to a fourth modified example using the three-clutch and three-brake of the embodiment apparatus.

FIG. 12 is a skeleton diagram showing a gear shift mechanism for an automatic transmission according to a fourth modified example using the two-clutch and three-brake of the embodiment apparatus.

FIG. 13 is a skeleton diagram showing a gear shift mechanism for an automatic transmission of a conventional device.

FIG. 14 is a collinear chart showing a state of member rotation at each gear stage in the shift control of the conventional device.

FIG. 15 is a diagram showing an engagement logic table at each gear in the shift control of the conventional device.

FIG. 16 is an engine torque characteristic diagram with respect to the engine speed using the throttle opening as a parameter.

[Explanation of symbols]

 a first planetary gear b second planetary gear c third planetary gear d first two-element connecting member e disconnecting clutch f clutch interlocking connecting member g second two-element connecting member h third two-element connecting member

Claims (3)

[Claims] 1. A single pinion type first planetary gear having a first sun gear, a first ring gear, and a first carrier holding a pinion meshing with both gears, a second sun gear, a second ring gear, and both gears. A single pinion type second planetary gear having a second carrier that holds a pinion that meshes with the third pinion type third planetary gear, a third sun gear, a third ring gear, and a third pinion type third planetary gear that holds a pinion that meshes with both gears. A planetary gear, a first two-element connecting member that integrally connects the first sun gear and the second sun gear, and a clutch intervening connecting member that connects the first carrier and the third ring gear via a disconnecting clutch. A second two-element connecting member that integrally connects the first ring gear and the second carrier, and the second ring gear and the third carrier together. A planetary gear train for an automatic transmission, comprising: a third two-element connecting member that is connected to the body. 2. The planetary gear train for an automatic transmission according to claim 1, wherein the first two-element connecting member is connected to an input shaft via a second clutch, and the third clutch connecting member is a third member. The ring gear side is connected to the output shaft, the second two-element connecting member is connected to the case via the first brake, and is connected to the input shaft via the third clutch. A connecting member is connected to the case via a second brake, the third sun gear is connected to the case via a third brake, and one gear is a three-clutch including the connecting / disconnecting clutch (first clutch). An automatic gear shift control means is provided, which is obtained by combining three of the three brakes and obtains a plurality of gears by an engagement release control rule without adjacent double gear shifts. Gear for machine Gearbox. 3. The planetary gear train for an automatic transmission according to claim 1, wherein the first two-element connecting member is directly connected to an input shaft, and the third ring gear side of the clutch interposition connecting member is an output shaft. The second two-element connecting member is connected to the case via the first brake and is connected to the input shaft via the third clutch, and the third two-element connecting member is connected to the second 2 out of 2 clutches 3 brakes including a connecting / disconnecting clutch (first clutch), one gear stage being connected to the case via a brake, the third sun gear being connected to the case via a third brake And a gear shift control means for obtaining a plurality of gear stages according to an engagement release control rule which does not cause double replacement in adjacent gear stages.