JPH0374666A - Planetary gear transmission device - Google Patents

Abstract

PURPOSE:To increase the degree of freedom of selection of a gear ratio without increasing the number of fastening elements by a method wherein eight members rotatable relatively to each other comprises seven rotary members containing input and output shafts and one stationary member, e.g. a case, and the number of the fastening elements necessary to form a shift step is set to five. CONSTITUTION:The positions of rotary members 1, 2, 3, 4, and 5 allotted according to a set number of teeth ratio are set at a lateral bar, and a rotation speed ratio is indicated at a longitudinal bar. Clutches C2 and C3+F1 are arranged to the rotary member 1, a clutch 1 to the rotary member 3, brakes B3 and F2 to the rotary member 4, and a brake B2 to the rotary member 5 to form an alignment chart on the left side. Further, rotary members 7, 5, and 6 are indicated at a lateral bar, the rotary member 7 is formed integrally with an input shaft IN, and a brake B1 is arranged to the rotary member 6 to form an alignment chart on the right side. As noted above, the number of fastening elements required for constitution of a shift step is left five, and an optimum target gear ratio is provided for all shift steps.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a planetary gear transmission, particularly to a planetary gear transmission used in a multi-stage automatic transmission for a vehicle.

(Prior art) As a conventional planetary gear transmission, for example,
There is a planetary gear transmission disclosed in Japanese Patent No. 149562, and one example of its configuration is a three-row single-binion type planetary gear train shown in FIG.

FIG. 15 is a collinear diagram of the example shown in FIG. 14.

The horizontal axis shows the positions of ■, ■, and ■ of the rotating members assigned according to the set tooth ratio, and the vertical axis shows the rotation speed ratio (= multi-rotation member rotation speed/input rotation speed).
A clutch C2 is placed on the rotating member ■, a brake B3 and a clutch C2 are placed on the rotating member ■, a brake B2 is placed on the rotating member ■, and the collinear diagram is shown on the left side.

A rotation speed ratio of 0 means fixed, and a rotation speed ratio of 1 means input rotation speed.

Similarly, the horizontal axis represents the rotating members (7), (7) is integrated with the input shaft, and the brake B1 is placed on the rotating member (2), making the collinear diagram on the right side.

In FIG. 15, there are six rotating members, and two of the six rotating members are restrained from rotating with two sets of fastening elements, and the other one is coupled to the input shaft to rotate integrally.
It constitutes a gear stage.

The rotating members are ■, ■, ■ and ■, ■ from the left in the figure.
,■, and the length of ■~■, the length of ■~■, and the length of ■~■
Let the ratio of the lengths be 1:A:B, and the lengths of ■～■ and ■
If the length ratio of ~■ is 〇, then the size of the planetary gear is a
(=number of sun gear teeth/number of ring gear teeth) is given by: q, =C, α2=8÷(1+A), a3=A. Note that the reason why the rotating member (3) is left blank is to establish a correspondence with the proposed invention.

The relationship between the gear stage and the state of the engagement element and the gear ratio of each stage are shown in the engagement logic table of FIG. 16.

(Problems to be Solved by the Invention) However, the above-mentioned conventional planetary gear transmission has a configuration having six rotating members including an input shaft and an output shaft, and has forward gears of 1st to 3rd, 5th to 6th. For a total of 7 speeds, 1st speed and 1st reverse, all gear ratios cannot be determined independently, and QI*Q2
* Since it is related under the three constraint condition expressions regarding α3 and is determined by the three variables A1 and C, the degree of freedom in selecting the gear ratio is low, and the target is set for all gear ratios. It is very difficult to set the gear ratio,
There has been a problem in that when a target gear ratio is selected at a certain gear, the gear ratio deviates from the target gear ratio at other gears.

For example, if the target gear ratio is set to 1st gear ratio = 3.0°, 2nd gear ratio = 1.9. Assuming 3rd gear ratio = 1.32,
A=0.5, B=0.61. C=0.954, and as a result, the fifth speed gear ratio=0.704 and the reverse speed gear ratio=2-50.

However, the target gear ratio for 5th gear (direction is 0.76~
Set it to 0.82, and set the reverse gear ratio value to 2.2.
If it is set to 5 to 4.2, the fifth gear ratio becomes a high gear, and insufficient driving force becomes a problem when driving at high speed.

As mentioned earlier, gear ratios are related to each other, so improving the 5th gear ratio will affect other gear ratios, and the affected gear ratios will deviate from the target gear ratio. Become.

For example, if the value of C is 1.6, 5th gear ratio = 0.
760 and the target value, but the third speed gear ratio = 1.223. The reverse gear ratio becomes 1.983, which deviates from the target gear ratio.

As a result, in the conventional device having S rotating members including the input/output shaft, as shown in FIG. This means that the degree of freedom in ratio selection is low, which is undesirable.

This invention was made by paying attention to the properties of such a collinear diagram of a gear train, and in a planetary gear transmission,
An object of the present invention is to increase the degree of freedom in gear ratio selection without increasing the number of fastening elements, and to make it easier to obtain the optimum target gear ratio at all gears.

(Means for Solving the Problems) In order to solve the above problems, in the planetary gear transmission of the present invention, the number of rotating members is increased by one, whereas the fastening elements necessary for configuring the gear stages are The number remained at five.

That is, a planetary gear is connected between an input shaft and an output shaft through which power is transmitted, and a plurality of fastening elements that can be selectively disconnected or connected are connected to the planetary gear, so that the input shaft and the output shaft are connected to each other. In a planetary gear transmission that achieves a plurality of forward gear ratios and one reverse gear ratio between the two, seven rotating members including the input shaft and the output shaft and one fixed member such as a case can rotate relative to each other. The collinear diagram shows that the number of fastening elements required to configure eight members and the gear stage is five.

(Function) When selecting a gear ratio in the planetary gear transmission of the present invention, the horizontal axis represents the position of the rotating member assigned according to the set gear ratio, and the vertical axis represents the rotational speed ratio. , if the rotation of two of the plurality of rotating members is restrained by two sets of fastening elements, and a collinear chart is drawn to show the fastening elements operating at each gear stage and the rotational speed ratio, the input/output shaft including 7
In the device of the present invention, which has two rotating members, the position of the rotating member assigned to the horizontal axis in the collinear diagram on the left is the 5th position, and the line that restricts the rotation of two of the rotating members by two sets of fastening elements is arranged. In other words, the degree of freedom in gear ratio selection is increased without increasing the number of fastening elements when compared with the conventional device, which has four positions on the collinear diagram on the left.

Therefore, it is possible to provide a planetary gear transmission having optimal target gear ratios at all speeds while being a simple and compact device without increasing the number of fastening elements.

(First example) First, a first example will be described.

FIG. 1 is a skeleton diagram showing a planetary gear transmission of a first embodiment corresponding to the invention described in claims 1, 2.3, 6.9.10.

The components include an input shaft IN and an output shaft OUT to which power is transmitted, a first planetary gear PG1, a second planetary gear PG2, and a third planetary gear PG3 connected between the input and output shafts IN and OUT. , the first clutch CI, the third clutch C3, the first brake 81, the second brake B2, . A third brake B3, a first one-way clutch Fl as a fastening element provided to improve gear shifting quality, a second one-way clutch C2 for controlling the engine brake, and the input shaft IN.
and seven rotating members (1), (2), (2), (2), (2), (2), (2), (2) including a member directly connected to the output shaft OUT, and one fixed member (2) fixed by the case.

The first planetary gear PGI is a double binion type,
The first carrier Pc supports the first sun gear S1, the first ring gear R1, and the two first binions PI+ and F12.
It has t.

The second planetary gear PG2 and the third planetary gear PG3 constitute one composite planetary gear, and the second ring gear R2, the common carrier PC that integrates the second carrier and the third carrier, and the second It has a sun gear S2, a third ring gear R3, and a third sun gear S3, and the common carrier PC has two short binions P2. F3 and Long Binion LP
is rotatably supported, and on the second planetary gear PG2 side, the second short pinion P2 meshes with the second ring gear R2 and long pinion LP, and the long pinion LP meshes with the second short pinion P2 and second sun gear S2 to transmit power. On the third planetary gear PG3 side,
The third shot pinion P3 connects with the third ring gear R3.
Sun gear S3 meshes with long pinion LP, and long pinion LP meshes with third short pinion P3 to transmit power.

The rotating member is connected to the third sun gear S3.

The rotating member (2) is connected to the common carrier PC and directly connected to the output shaft 0LIT.

The rotating member (2) is connected to the third ring gear R3.

The rotating member (2) is connected to the second ring gear R2.

The rotating member (2) is connected to the first ring gear R1 and the second sun gear S2.

The rotating member (2) is connected to the first carrier PCI.

The rotating member (7) is connected to the first sun gear S1 and directly connected to the input shaft IN.

Next, the relationship between these rotating members and fastening elements will be explained.

The first clutch C1 includes a rotating member ■ and a rotating member ■
to disconnect and disconnect from

The second clutch C2 includes a rotating member ■ and a rotating member ■
to disconnect and disconnect from

The third clutch C3 and the first one-way clutch E1 are arranged in series and connect and disconnect the rotating members (1) and (2).

The first brake B1 consists of a rotating member ■ and a fixed member ■
to disconnect and disconnect from

The second brake B2 consists of a rotating member ■ and a fixed member ■
to disconnect and disconnect from

The third brake 83 and the second one-way clutch F2 are connected in parallel to connect and disconnect the rotating member (4) and the fixed member (2).

Next, the effect will be explained.

FIG. 2 shows a collinear diagram of the embodiment device.

The horizontal axis shows the positions of the rotating members ■, ■, ■, ■, ■, which are assigned according to the set tooth ratio, and the vertical axis shows the rotation speed ratio (
= rotational speed of each rotating member/input rotational speed), and C2 and e3+F1. The rotating member ■ has CI, and the rotating member ■ has B3 and F2. B2 is placed on the rotating member ■, and the collinear diagram is on the left side.

A rotational speed ratio O means fixed, and a rotational speed ratio 1 means an input rotational speed.

Similarly, rotating members (7), (7), and (2) are taken on the horizontal axis, and the rotating member (7) is integrated with the input shaft IN.

Figure 3 shows a conclusion logic table.

The first speed is obtained by connecting C2 and 83.

The second speed is obtained by connecting C2 and 82.

Third speed is obtained by connecting C2 and 81.

Fourth speed is obtained by connecting C2 and 01.

Fifth speed is obtained by connecting C1 and 81.

Fifth speed is obtained by connecting C1 and 82.

Reverse speed is obtained by connecting 81 and 83.

The seventh speed is obtained by connecting C1 and 83, but is omitted in this example in view of the gear ratio balance.

Neutral can be achieved by not engaging any engagement elements or by engaging one engagement element, but in this example, B3 is set so that it is only necessary to engage one engagement element when shifting to first and reverse speeds. Let's conclude.

In this way, the gear ratio at each gear stage is obtained as shown on the right side of FIG.

In this gear ratio formula, α=(number of sun gear teeth ÷ number of ring gear teeth), Q1Q2. C3, are the first
．． Second. Third planetary gear PG1. This is for PO2, PO2. Regarding k, see 2nd. 3rd ring gear R
2, R3, a virtual fourth network configured by a common carrier PC
for a planetary gear, where ZaZo; 2nd. Number of teeth of 3rd ring gear, zP□, Zps: 2nd. Third
The number of teeth on the long pinion LP that meshes with the planetary gear.

Note that the following constraint condition expression applies to the virtual fourth planetary gear.

No-kNA=(1k)Nc As explained above, the planetary gear transmission of the first embodiment has the features listed below.

■ Since the device has seven rotating members including the input and output shafts, the number of fastening elements required to configure six forward speeds and one reverse speed is the same as the conventional device, without increasing the number of five. By increasing the degree of freedom in gear ratio selection, it is possible to easily obtain the optimum target gear ratio at all gears.

That is, in the planetary gear transmission of the first embodiment, which has seven rotating members including the input and output shafts, the positions of the rotating members allocated to the horizontal axis are five, as shown in the collinear diagram on the left side of FIG. The degree of freedom in how to draw a line that restricts the rotation of two of the rotating members by two sets of fastening elements, that is,
When compared with the conventional device, which has four positions on the collinear chart on the left, the degree of freedom in gear ratio selection increases without increasing the number of fastening elements. This is also clear from the fact that k is included in addition to C1, C2, and α, as shown in the formula.

■ The second planetary gear PG2 and the third planetary gear PG3 have a long pinion LP spanning them, and are composite planetary gears consisting of five rotating members that can rotate relative to each other, so they do not include input/output shafts. Although the seven rotating members are configured by three sets of planetary gears, which have the same appearance as the conventional device, the device can be made more compact by shortening the axial dimension.

■ A shift from each forward gear ratio to the next higher or lower gear ratio involves a change from engagement to disengagement of one engagement element and non-engagement of another engagement element, as shown in Figure wJ3. Since this is achieved through two changes: from to engagement, it is easy to ensure quality shifting.

■ One-way clutches Fl and F2 are not directly related to configuring gears, but one-way clutch F1 can prevent engine braking from being applied to drive input from the wheels and impairing drivability. Furthermore, as a secondary effect, the 4-5 shift can be changed to a one-way clutch shift, making it easier to ensure shift quality.

Further, the one-way clutch F2 can ensure shift quality by using the one-way clutch shift for the 1st-2nd shift with a large torque step.

(Second example) Next, the 'lA2 embodiment will be explained.

FIG. 4 is a skeleton diagram showing a second embodiment of the planetary gear transmission corresponding to the invention set forth in claim 1.2.4.7.

Although parts related to the one-way clutch are omitted in FIG. 4, the essential difference in the configuration compared to FIG. 1 is that one brake is eliminated and one clutch is added.

With such a configuration, the collinear diagram shown in FIG. 5 is obtained, and a gear ratio equivalent to that of the first embodiment device can be obtained. The fastening logic of this embodiment is shown in Figure 6. This second embodiment device can have all of the features of the first embodiment device, and has an advantage over the first embodiment device. This has the advantage of keeping the rotation of the rotating member ■ small at high speeds.

(Third example) Next, a third example will be described.

FIG. 7 is a skeleton diagram showing a third embodiment of the planetary gear transmission corresponding to the invention described in claims 1, 2.4.

This third embodiment device has a first planetary gear PG in order to create the same relationship between rotating members
I is replaced with another gear train.

That is, the first planetary gear PGI of the third embodiment has two first planetary gears PGI.
It is composed of Sungear 5ILS12 and one carrier PCI, and the carrier PCI has a long binion L.
One PI and one short pinion P1 are rotatably attached.

Similarly, the same rotating members ■, ■, ■ as in the second embodiment device
In order to create the relationships of , ■, and ■, the composite planetary gears forming the second planetary gear PG2 and the third planetary gear PG3 were replaced with another gear train.

That is, one long pinion LP2 and one short pinion P2 having different numbers of teeth are rotatably supported by a common carrier PC2, and a rotating member (2).

The planetary gear consisting of ■ and ■ is given by the double binion constraint equation, and the rotating member, ■.

The planetary gear composed of ■ is given by a single-binion constraint formula, and the virtual planetary gear composed of rotating members ■, ■, and ■ is given by a double-binion constraint formula. become equivalent.

In this way, the apparatus of the second embodiment becomes equivalent, so that FIGS. 5 and 6 can be applied to this embodiment.

(Fourth example) Next, a fourth example will be described.

FIG. 8 is a skeleton diagram showing a third embodiment of the planetary gear transmission corresponding to the invention described in claims 1, 2.4.

This third embodiment device uses composite planetary gears that constitute the second planetary gear PG2 and the third planetary gear PG3 in order to create the same relationship of ■, ■, ■, ■ of the rotating members as in the second embodiment. , was replaced by another gear train consisting of one double-binion planetary gear and two single-binion planetary gears.

In FIG. 8, from the left, the first to fourth planetary gears PG1. If we call it PO2゜PO2, PO2, the rotating member ■ is the second
~4th Sangia S2. S3. The rotating member (2) is a combination of the second ring gear R2, the third carrier PC3, the fourth carrier PC4, and the output shaft OUT, and the rotating member (■) is the fourth ring gear R4.
The rotating member (2) is connected to the third ring gear R3, and the rotating member (2) is an integral unit of the second carrier PC2 and the first ring gear R1.

In this way, the apparatus of the second embodiment becomes equivalent, so that FIGS. 5 and 6 can be applied to this embodiment.

(Fifth example) Next, a fifth example will be described.

FIG. 9 is a skeleton diagram showing a fifth embodiment of the planetary gear transmission corresponding to the invention described in claims 1, 2, and 5.8.

The components include an input shaft IN and an output shaft OUT to which power is transmitted, a first planetary gear PGI, a second planetary gear PG2, and a third planetary gear PG3 connected between the input and output shafts IN and OUT. , the first clutch CI, I! as a fastening element necessary to achieve the forward gear ratio of S speed and the reverse gear ratio of 1st speed! 2nd clutch C2, 3rd clutch C3, 1st
Seven rotating members ■, ■, ■, ■, ■, ■ including a brake Bl, a second brake B2, and a member directly connected to the input shaft IN and output shaft OUT.

■ and one fixed member ■ depending on the case.

The first planetary gear PGI is a double pinion type,
The first carrier Pc supports the first sun gear S1, the first ring gear R1, and the two first pinions Pit and PI3.
It has t.

The second planetary gear PG2 and the third planetary gear PG3 constitute one composite planetary gear, and the second ring gear R2, the common carrier PC that integrates the second carrier and the third carrier, and 1! 2 sun gear S2 and 3rd ring gear R3
and a third sungear S3, and the common carrier PC has two
Two short binions P2. P3 and long pinion L
P is rotatably supported, and on the second planetary gear PG2 side, the second shot pinion P2 is connected to the second ring gear R2.
meshes with the long-binion LP, and the long-binion LP
meshes with the second short pinion P2 and second sun gear S2 to transmit power, and on the third planetary gear PG3 side, the third short pinion P3 meshes with the third ring gear R3, third sun gear S3, and O pinion LP, The long pinion LP meshes with the third short pinion P3 to transmit power.

The rotating member (2) is connected to the third sun gear s3.

The rotating member (2) is connected to the common carrier PC and to the output shaft 0LIT.

The rotating member (2) is connected to the third ring gear R3.

The rotating member (2) is connected to the second ring gear R2.

The rotating member (2) is connected to the second sun gear s2.

The rotating member (2) is connected to the first sun gear s1 and is also connected to the input shaft IN.

The rotating member (7) is connected to the first ring gear R1.

The fixed member (2) is connected to the first carrier Pc1.

Next, the relationship between these rotating members and fastening elements will be explained.

The first clutch C1 connects and disconnects the rotating member (2) and the input shaft IN.

The second clutch C2 connects and disconnects the rotating member (2) and the input shaft IN.

The third clutch C3 consists of rotating member ■ and rotating member ■
Control the connection/disconnection with.

The first brake B1 connects and disconnects the rotating member (4) and the case.

The second brake B2 connects and disconnects the rotating member (2) and the case.

Next, the effect will be explained.

FIG. 10 shows a collinear diagram of the example device.

The horizontal axis shows the positions of the rotating members ■, ■, ■, ■, ■, which are assigned according to the set tooth ratio, and the vertical axis shows the rotation speed ratio (
(2) each rotating member rotation speed/input rotation speed), and CI for the rotating member (2).

C2 is placed on rotating member ■, B2 is placed on rotating member ■ by 81 degrees, and B2 is placed on rotating member ■, making the collinear diagram on the left side.

A rotational speed ratio O means fixed, and a rotational speed ratio 1 means an input rotational speed.

Similarly, the rotating members ■, ■ and the fixed member ■ are placed on the horizontal axis, the rotating member ■ is a member that rotates together with the input shaft IN, and C3 is placed between the rotating members ■ and ■. Let it be a collinear diagram.

FIG. 11 shows a conclusion logic table.

The first speed is obtained by connecting C1 and 81.

The second speed is obtained by connecting C1 and 82.

Third speed is obtained by connecting C1 and 03.

4th speed is obtained by connecting C2 and 03.

5th speed is obtained by connecting C2 and 03.

6th speed is obtained by connecting C2 and 82.

Reverse speed is obtained by connecting 81 and 03.

The seventh speed is obtained by connecting C2 and 81, but is omitted in this example in view of the gear ratio balance.

Neutral can be achieved by not engaging any engagement elements or by engaging one engagement element, but in this example, B1 is set so that it is only necessary to engage one engagement element when shifting to first and reverse speeds. Let's conclude.

In this way, each gear has exactly the same gear ratio as in the first embodiment shown on the right side of FIG.

As explained above, in the planetary gear transmission of the fifth embodiment, the effects of (1) and (2) in the first embodiment are different from those of the first embodiment.

It goes without saying that it has the features described in (2), but also has the additional features described below.

In the device of the fifth embodiment, the rotating member ■ can be separated from the rotating member ■ by the third clutch C3, and since the rotating member ■ is always connected to the input shaft IN and the fixed member ■ is always connected to the case, The rotating member (7) always maintains a constant speed ratio with respect to the input shaft IN.

As a result, as is clear from comparing the collinear diagram of FIG. 10 and the collinear diagram of FIG. 2, in the case of the fifth embodiment device, the rotation of the member of the first planetary gear PGI becomes negative. This prevents the rotational speed of the pinion from increasing, which is advantageous in terms of gear noise compared to the device of the first embodiment.

(6th example) Next, a sixth embodiment will be described.

FIG. 12 is a skeleton diagram showing a planetary gear transmission according to a sixth embodiment of the invention corresponding to claims 1, 2.5.

This sixth embodiment device is replaced with another gear train to create the same relationship between rotating members ■, ■, ■, ■, ■ as in the fifth example device, and creates a relationship between members ■, ■, ■. first for
The planetary gear PG+ is replaced with another gear train.

That is, in order to make the relationship between the rotating members ■, ■, ■, ■, and ■ equivalent to that of the fifth embodiment, one long pinion LP and one short pinion P2 with different numbers of teeth are connected to the carrier P.
The long pinion LP meshes with the second ring gear R2 of the second planetary gear PG2 and the short pinion P2, and the single pinion P2 engages with the long pinion LP and the second sun gear S2 of the second planetary gear PG2. One long pinion LP, which is configured to mesh with each other and has a different number of teeth, is connected to the IiS sun gear S3 of the third planetary gear PG3 and the third pinion LP.
It is configured to mesh with the third ring gear R3 of the planetary gear PG3.

With this configuration, the planetary gears constituted by rotating members ①, ②, ②, second ring gear R2, second sun gear S2, . Create a double binion constraint expression corresponding to the carrier PC.

Further, the planetary gears consisting of ■ and ■ of the rotating members are respectively third sun gears S3. A single-binion constraint condition expression is created corresponding to the third ring gear R3 and the carrier PC.

In addition, the virtual planetary gears composed of rotating members ■, ■, ■ are the third ring gear R3 and the second ring gear R, respectively.
2. Create a double binion constraint expression corresponding to the carrier PC.

As a result of the above, a composite planetary gear train equivalent to the device of the fifth embodiment is obtained.

On the other hand, regarding the relationship between members ■, ■, and ■, it is composed of a single-binion planetary gear, and members
are respectively the first sun gear S1. Corresponds to carrier PCI and ring gear R1, and creates a single-binion restraint type.

In this way, a collinear diagram equivalent to the device of the fifth embodiment is obtained,
10 and 11 can be applied to this example and have the same characteristics as the fifth embodiment. In addition, in this sixth embodiment, the fifth
The number of binions can be reduced compared to the embodiment.

(Seventh Example) Next, a seventh embodiment will be described.

FIG. 13 is a skeleton diagram showing a planetary gear transmission according to a seventh embodiment of the invention corresponding to claims 1, 2.5.

This seventh embodiment device uses composite planetary gears constituting the second planetary gear PG2 and the third planetary gear PG3 in order to create the same relationship between the rotating members ■, ■, ■, ■, ■ as in the fifth embodiment. , replaced by another gear train consisting of one double-binion planetary gear and two single-binion planetary gears.

In Fig. 13, from the left, the 1st to 4th planetary gears PGM, PO2
゜If we call it PO2, PO2, then the rotating member ■ is the second to fourth sun gear S2. S3. S4 is integrated, and the rotating member (2) is the second ring gear R2 and the third ring gear.
Carrier PC3, fourth carrier PC4, and output shaft OUT are integrated, and rotating member ■ is the fourth ring gear R.
The rotating member ■ is connected to the third ring gear R3, and the rotating member ■ is connected to the second ring gear R3.
It is connected to the carrier PC2.

The relationship between the members (2), (2), and (2) is the same as in the fifth embodiment, which is comprised of the double-binion type first planetary gear PG+.

In this way, a collinear diagram equivalent to the device of the fifth embodiment is obtained,
10 and 11 can be applied to this example and have the same characteristics as the fifth embodiment. In addition, in this seventh embodiment, the fifth
Compared to the embodiment, all gears can be simple planetary gears.

Although the embodiments of the present invention have been described above with reference to the drawings, the specific gear train and the arrangement of the fastening elements are not limited to the embodiment device. A planetary gear transmission is included in the present invention if it constitutes eight members that are rotatable relative to each other with one fixed member such as a case, and the number of fastening elements required to configure a gear stage is five. .

(Effects of the Invention) As explained above, in the planetary gear transmission of the present invention, the number of rotating members is increased by one to seven, whereas the number of fastening elements required to configure a gear stage is Since the number of fastening elements remains unchanged at five, the degree of freedom in gear ratio selection is increased without increasing the number of fastening elements, and the effect is that it is possible to easily obtain the optimum target gear ratio at all gears.

[Brief explanation of drawings]

Fig. 1 is a skeleton diagram showing the planetary gear transmission of the first embodiment, Fig. 2 is a collinear diagram of the device of the first embodiment, and Fig. 3 is a diagram showing a fastening logic table of the device of the first embodiment. , FIG. 4 is a skeleton diagram showing the planetary gear transmission of the second embodiment, FIG. 5 is a collinear diagram common to the devices of the second to fourth embodiments, and FIG.
FIG. 7 is a skeleton diagram showing the planetary gear transmission of the third embodiment; FIG. 8 is a skeleton diagram of the planetary gear transmission of the fourth embodiment. , FIG. 9 is a skeleton diagram showing the planetary gear transmission of the fifth embodiment, FIG. 10 is a collinear diagram common to the devices of the fifth to seventh embodiments, and FIG. 11 is a diagram showing the devices of the fifth to seventh embodiments. FIG. 12 is a skeleton diagram showing the planetary gear transmission of the sixth embodiment, FIG. 13 is a skeleton diagram of the planetary gear transmission of the seventh embodiment, and FIG. 14 is a skeleton diagram showing the planetary gear transmission of the seventh embodiment. Skeleton diagram showing a conventional planetary gear transmission, I! FIG. 15 is a collinear diagram for the conventional device, and FIG. 16 is a diagram showing a conclusion logic table for the conventional device. IN...Input shaft OUT...Output shaft PGI...First planetary gear PO2...Second planetary gear PO2...Third planetary gear GV, C2, C3...Clutch (clutching element) 81 ,
82.83...Brake (fastening element)■,■,■,■
, ■, ■, ■... Rotating member ■... Fixed member

Claims (1)

[Scope of Claims] 1) A planetary gear is connected between an input shaft and an output shaft through which power is transmitted, and a plurality of fastening elements that can be selectively disconnected or engaged are connected to the planetary gear, and the A planetary gear transmission that achieves a plurality of forward gear ratios and one reverse gear ratio between an input shaft and an output shaft, comprising seven rotating members including the input shaft and the output shaft, and one fixed member such as a case. A planetary gear transmission comprising eight members rotatable relative to each other and five fastening elements required to form a gear stage. 2) In the planetary gear transmission described in item 1 above, the shift from each forward gear ratio to the next higher or lower gear ratio involves a change from engagement to disengagement of one engagement element and a change in the engagement of the other engagement element. A planetary gear transmission characterized in that the change is achieved by two changes: a change from non-engagement to engagement of two engagement elements. 3) In the planetary gear transmission described in item 1 above, the seven rotating members are (1), (2), (3), (4), (
5), (6), and (7), and the fixed member is named (8), and if (2) contains the output shaft and (7) contains the input shaft, then on the collinear diagram ( 1), (2), (3)
, (4), (5) in this order, (7), (5)
, (6) are arranged in this order, a fastening element that connects and disconnects (1) and (7), a fastening element that connects and disconnects (3) and (7), (
4) and (8), a fastening element that connects and disconnects (5) and (8), and a fastening element that connects and disconnects (6) and (8). A planetary gear transmission characterized by comprising: 4) In the planetary gear transmission described in item 1 above, the seven rotating members are (1), (2), (3), (4), (
5), (6), and (7), and the fixed member is named (8), and if (2) contains the output shaft and (7) contains the input shaft, then on the collinear diagram ( 1), (2), (3)
, (4), (5) in this order, (8), (5)
, (6) are arranged in this order, a fastening element that connects and disconnects (1) and (7), a fastening element that connects and disconnects (3) and (7), (
4) and (8), a fastening element that connects and disconnects (5) and (8), and a fastening element that connects and disconnects (6) and (7). A planetary gear transmission characterized by comprising: 5) In the planetary gear transmission described in item 1 above, seven rotating members and one fixed member are provided in (1) and (2).
, (3), (4), (5), (6), (7), and (8), where (2) includes the output axis, (6) includes the input axis, and (8) the case. If it contains (1), (2), (3), (4), (5) in this order on the collinear chart, (6), (7), (8) are arranged in this order, (1), (2), (3), (4), and (5) are represented by one line on this collinear diagram, and (6), (7), ( 8) is represented by another line, a fastening element that connects and disconnects (1) and the input shaft,
A fastening element that connects and disconnects (3) and the input shaft, a fastening element that connects and disconnects (5) and (7), a fastening element that connects and disconnects (4) and the case, and a fastening element that connects and disconnects (5) and the case. 1. A planetary gear transmission characterized by having a planetary gear train configured as shown in the diagram. 6) In the planetary gear transmission according to item 3 above, members (1), (2), (3), (4), and (5) are constituted by one composite planetary gear, and members (7), ( 5),
A planetary gear transmission characterized in that (6) is configured by one simple planetary gear. 7) In the planetary gear transmission according to the above item 4, the members (1), (2), (3), (4), and (5) are constituted by one composite planetary gear, and the members (8), ( 5),
A planetary gear transmission characterized in that (6) is configured by one simple planetary gear. 8) In the planetary gear transmission according to item 5 above, members (1), (2), (3), (4), and (5) are constituted by one composite planetary gear, and members (6), ( 7),
A planetary gear transmission characterized in that (8) is constituted by one simple planetary gear. 9) In the planetary gear transmission described in items (3), (4), and (5) above, a friction engagement element capable of restraining rotation in both directions and a one-way clutch are arranged in series, and further in parallel therewith, a friction engagement element capable of restraining rotation in both directions is arranged in series. A planetary gear transmission characterized in that a frictional fastening element capable of restraining the rotation of is arranged to constitute a fastening element that connects and disconnects the input shaft from (1). 10) In the planetary gear transmission described in items 3, 4, and 5 above, a friction engagement element capable of restraining rotation in both directions and a one-way clutch are arranged in parallel, and a coupling element for connecting and disconnecting the case with (4) is provided. A planetary gear transmission characterized by comprising: