JPH0392650A - Epicyclic gear type multistage transmission - Google Patents

Abstract

PURPOSE:To make a multistage transmission compact by changing the speed at multiple stages more than five-stage with two-stage gear lines. CONSTITUTION:Four rotary elements of a sun gear 1S of a first gear line 1, a first connecting member 31, an epicyclic gear holding member 2C of a second gear line 2 and a second connecting member 32 are formed in gear relation, while three rotary elements except for the second connecting member 32 as an output shaft, namely, the sun gear 1S of the first gear line 1, the first connecting member 31 and the epicyclic gear holding member 2C of the second gear line 2 can be respectively connected to an input shaft with a clutch mecha nism and also can be fixed by brake. As a result, any rotary elements are rotated synchronously with the input shaft through the clutch mechanism, while one of other rotary elements is fixed by operating the brake to drive the second connecting member 32 as an output shaft for rotation through a different six- stage torque transmitting passage.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a planetary gear type transmission used in automatic transmissions of automobiles, etc., and more particularly to a planetary gear type multi-stage transmission with a multi-stage number of gears.

[Prior Art and Problems Therewith] Conventionally, automatic transmissions for vehicles have generally included a gear type transmission in a downstream stage of a torque converter.

A gear type transmission used in such an automatic transmission has a planetary gear meshed with a sun gear disposed in the center and a ring gear coaxially disposed outside the sun gear. A predetermined gear ratio is obtained by fixing one of the gears.

Generally, the gear train consisting of the sun gear, planetary gear, and ring gear described above is arranged in two rows, and any gears are fixed or connected to form three to four forward stages and one reverse stage. There are many.

By the way, in a vehicle that uses an engine as a power source, from the viewpoint of effective use of the power, it is desirable to increase the number of gears and always use the rotation range where the engine output is highest. This also provides secondary effects such as improved quietness and fuel efficiency. In the case of a manual transmission, there is a problem in that increasing the number of gears makes the operation complicated, but in the case of an automatic transmission, such a problem does not exist, and its realization has been desired.

As a gear-type transmission device that enables such multi-stage transmission, there is one that has a three-stage gear train, as disclosed in Japanese Patent Publication No. 53-21511.

However, IT et al., increasing the number of gear trains like this,
Transmissions were inevitably longer and needed to be stronger, so there was an assumption that they would be larger. 4,
In addition, it is difficult to apply a front-wheel drive type with a transversely mounted engine because the length of the transmission is restricted by the width of the vehicle, and there is a desire to develop a multi-speed transmission that can be configured in a compact size. Ta.

[Object of the Invention] The present invention solves the above problems 1+! } In view of the above, an object of the present invention is to provide a planetary gear type multi-stage transmission that can be constructed in a small size.

[Structure of the Invention] For this reason, the Dashi Dashi type multi-stage transmission according to the present invention has a first gear train in which one planetary gear is meshed and interposed between the sun gear and the ring gear on the outside of the input shaft. , a second gear train is configured and arranged, in which a pair of planetary gears meshing between the sun gear and the ring gear are interposed, and the planetary gear holding member of the first gear train and the sun gear of the second gear train are connected by a first connecting member, and the ring gear of the first gear train and the ring gear of the second gear train are connected by the second connecting member, and the input shaft, the sun gear of the first gear train, A clutch mechanism is interposed between the first connecting member and the planetary gear holding member of the second gear train, each of which is capable of holding both members in a relatively non-rotatable manner, and
The sun gear of the first gear train, the first connecting member, and the planetary gear holding member of the second gear train are each provided with a braking mechanism capable of regulating rotation thereof, and the second connecting member is configured as an output shaft. It is something.

According to the above configuration, four rotating elements are configured in a single-coupling relationship: the sun gear of the first gear train, the first connecting member, the planetary gear holding member of the second gear train, and the second coupling member. In addition, excluding the second connecting member which is the output shaft, the other three rotating elements, namely the sun gear of the first gear train, the first connecting member, and the planetary gear holding member of the second gear train, are It can be independently coupled to the input shaft by a clutch mechanism and can be fixed by a braking device.

By connecting the clutch mechanism of any rotating element to rotate it in synchronization with the input shaft, and fixing the force of one of the other rotating elements by applying a braking mechanism, six different stages of rotation can be achieved. The second connecting member, which is the output shaft, is rotationally driven via the force transmission path. Furthermore, by simultaneously connecting the clutch mechanisms of any two rotating elements and causing them to rotate synchronously with the input shaft, the second connecting member (output shaft) also rotates synchronously with the input shaft via the two rotating elements (i.e., directly connected). state).

Therefore, by appropriately setting the gear ratios of these gears, a transmission with seven gear ratios can be configured, and by setting one of the gears as reverse, a multi-stage transmission with six forward gears and one reverse gear can be configured. It is something that can be done.

[Embodiments of the invention] Embodiments of the present invention will be described below based on the drawings.

FIG. 1 is a schematic diagram showing a schematic configuration of a planetary gear type multi-stage transmission according to the present invention.

The illustrated transmission is configured such that a first gear train 1 and a second gear train 2 are arranged in a row, and an input shaft 10 is arranged in the center of the first and second gear trains 1.2. ing.

The first gear train l includes a sun gear IS, which is an outer gear, and a ring gear IR, which is an inner gear arranged concentrically outside the sun gear IS. They are meshed and connected via gear IP.

A plurality of planetary gears (for example, three) are arranged at equal intervals in the circumferential direction of the sun gear IS and the ring gear IR, and these planetary gears IP are attached to a ring-shaped carrier Ic serving as a holding member while keeping their relative positions unchanged. It is held so that it can rotate freely.

Therefore, by fixing the carrier IC so that it cannot rotate, Sankia I
When S is rotated, the rotational force is transmitted to the ring gear IR via the planetary gear IP, and the ring gear IR rotates in the opposite direction to the sun gear Is.

In the second gear train 2, similarly to the first gear train 1 described above, a ring gear 2R is arranged concentrically on the outside of the sun gear 2S, and the ring gear 2R is held in mesh with the carrier 2C between the two gears 2S and 2R. A pair of planetary gears 21F and 22F are interposed, and the sun gear 2S and ring gear 2R are connected to the planetary gear 21P. They are interlocked and connected via 22F. Therefore, when the carrier 2C is fixed non-rotatably and the sun gear 2S is rotated, the rotational force is transmitted to the ring gear 2R via the planetary gears 21F and 22F, so that the ring gear 2R rotates in the same direction as the sun gear 2S. This is what has become.

Incidentally, the planetary gears 21F and 22F are arranged in plural pairs at equal intervals in the circumferential direction of the sun gear 2S and the ring gear 2R, similar to the planetary gear IP of the first gear train. The carrier 1C of the first gear train 1 and the sun gear 2S of the second gear train 2 are connected by a first connecting member 31, and the ring gear IR of the first gear train 1 and the ring gear 2R of the second gear train 2 are They are connected by a connecting member 32.

Moreover, between the input shaft 10, the sun gear IS of the first gear train l, the first connecting member 31, and the carrier 2C of the second gear train 2,
Clutches Kl, K2, K as clutch mechanisms, respectively
3 is interposed. These respective clutches Kl, K2
, K3, each member rotates integrally with the input shaft 10, and by disconnecting the clutches K1, K2, and K3, each member becomes rotatable.

Furthermore, the sun gear 13 of the first gear train 1, the carrier IC (i.e., the first connecting member 31) of the first gear train 1, and the second gear train 2
Brakes Bl, B2, and B3 as braking mechanisms for fixing the carrier 2C in a non-rotatable manner are installed and arranged in a mission case (not shown). When the respective brakes Bl, B2, and B3 are applied, the corresponding members are fixed in a non-rotatable manner.

In the transmission device according to the above structure, by connecting the clutch Kl, the input shaft 10 and the carrier IC of the first gear train 1 are coupled, and rotational force is input from the carrier IC. Rotational force is input from the first connecting member 3l by connecting K2, and from the carrier 2C of the second gear train 2 by connecting clutch K3.

Here, the speed ratio calculated from the gear ratio between each of the above elements (the sun gear S, the first connecting member 3l and the carrier 2C as the input side, and the second connecting member 32 as the output side) is shown in FIG. The settings are as shown in the speed diagram. That is, the second
In the figure, the intervals between vertical lines indicating each element correspond to the speed ratio of each element.

In the planetary gear type multi-stage transmission configured as described above, by selectively operating the clutches Kl, K2, K3 and the brakes Bl, B2, B3 as shown in FIG. It is possible to shift into 6 gears and 1 reverse gear. Note that rOJ in the figure indicates the effect.

That is, in the first speed (1st), the clutch K1 and the brake B3 are applied to input rotational force from the sun gear IS of the first gear train 1, and the carrier 2C of the second gear train 2 is fixed. As a result, the sun gear 1S rotates the ring gear IR (i.e., the second connecting member 32) of the first gear train 1 via the planetary gear IP of the first gear train 1, and the rotation of the second connecting member 32 is caused by the rotation of the second connecting member 32. Planetary gears 21P, 22 of 2nd gear train 2
Since the sun gear 2S of the second gear train 2 is rotated via F, the second connecting member 32 will rotate at the combined speed of both gears.

In the speed diagram shown in the second diagram, the second connecting member 3 which is the output shaft
2, the speed of the second connecting member 32 is rlJ.
(<The position where the line connecting the r position and the fixed side carrier 2C to the rOJ position is extended and intersects the input side sun gear IS line indicates the speed (rotation speed) of the sun gear IS. According to this, the rotation speed of the sun gear Is, which is the input side, is higher than the rotation speed of the second connecting member 32, which is the output shaft, that is, the reduction ratio is high.

Although it will not be explained in detail below, it can be read in the same way at all gears.

In the second speed (2nd), the clutch K3 and the brake B2 are applied to input rotational force from the carrier 2C of the second gear train 2, and the first connecting member 3l is fixed. As a result, the planetary gear 21F of the second gear train 2 rotates in relation to the rotation l1 of the carrier 2C and the fixed sun gear 23 (first connecting member 31),
The ring gear 2R (ie, the second connecting member 32) of the second gear train 2 is rotated via 22F. In the second illustrated speed diagram, the rOJ of the first connecting member 31 which is fixed is
The position where the extension of the line connecting rlJ and rlJ of the second connecting member 32 intersects the line of the carrier 2C on the input side is the carrier 2
It is the rotation speed of C.

In 3rd gear (3rd), clutch K2 and brake B3
is applied to input rotational force from the first connecting member 3l, and at the same time, the carrier 2C of the second gear train 2 is fixed. The sweetfish, the first series sweetfish member 31 (sun gear 2S) rotates the planetary gears 21F, 22F of the second gear train 2, and the planetary gear 2
The ring gear 2R (ie, the second connecting member 32) of the second gear train 2 is rotated by the rotation of 1P and 22F.

In 4th gear (4th), clutch K3 and brake B1
to input rotational force from the carrier 2C or 12 of the second gear train 2, and fix the sun gear IS of the first gear train 1. As a result, due to the rotation of the planetary gears 21F and 22F of the second gear train 2 due to the rotation of the carrier 2C,
Sun gear 2S of second gear train 2 (i.e. first connecting member 31)
and the ring gear IR of the second gear train 2 (i.e., the second connecting member 3
2) is rotated and the first gear train 1 is fixed.
The ring gear IR (i.e., the second connecting member 32) of the first gear train 1 is rotated by the planetary gear IF that rotates due to the rotation of the first connecting member 3l in relation to the sun gear Is, and both rotational force transmission paths are rotated. The second coupling member 32 is rotated in a state in which the rotational forces from the two are combined.

In the fifth speed (5th), the clutches K2 and K3 are activated, and rotational force is input from both the sun gear 2S of the second gear train 2 (i.e., the first connecting member 31) and the carrier 2C of the second gear train 2. As a result, the first connecting member 31 and the carrier 2C will rotate synchronously, and therefore the planetary gears 21F and 22F of the second gear train 2 will not rotate (rotate).
The second connecting member 32 also rotates synchronously. That is, in the fifth speed, the input and output are directly connected. Note that the combination of clutches that are activated to directly connect input and output in this way is not limited to clutch K2 and clutch K3. It's a good thing.

In 6th gear (6th), clutch K2 and brake B1
When the rotational force is input from the first connecting member 31, the sun gear Is of the first gear train 1 is fixed. As a result, the planetary gear IP of the first gear train 1 rotates in relation to the sun gear IS of the first gear train 1, which is fixed by the rotation of the first connecting member 3l, and the rotation of the planetary gear IP causes the first gear Ring gear IR of row 1 (i.e. second connecting member 32)
is rotated.

In reversing (Rev), the clutch K1 and the brake B2 are applied, the rotation force is input from the sun gear IS of the first gear train 1, and the first connecting member 31 is fixed. As a result, the ring gear IE (ie, the second connection member 32) of the first gear train 1 is rotated by the planetary gear IP of the first gear train 1 rotated by the sun gear IS.

Here, in the second illustrated speed diagram, the direction of the line connecting rlJ of the second connecting member 32 and rOJ of the carrier IC is downward IF.
This indicates that the input shaft 1o and the output shaft (second connecting member 32) are rotated in opposite directions.

Other embodiments of the present invention are shown in Figures t54 to 5.

This is to reduce the shift shock when shifting.
Clutches Kl', K2', K3' and brakes Bl', B2' are installed in parallel with the clutches Kl, K2, K3 and brakes Bl, B2, B3, respectively, in the first embodiment described above.
, B3', and the newly installed clutch Kl
', K2', K3' and brake Bl', B2
', B3' are each provided with a one-way clutch OW...

The coupling rotation direction of the one-way clutch OW is the input shaft lO.
The rotation of the input shaft can be transmitted to the driven side (that is, l5 is engaged), and vice versa, it is not engaged (that is, the input shaft is not rotationally driven by the rotational force of the driven side).

Then, when shifting, first the one-way clutch OW
By applying the clutch or brake on the side where the driven side is interposed, it is possible to prevent shift shock caused by sudden application of rotational resistance on the driven side. However, in this state, the engine brake does not fully operate, so when the gear position, vehicle speed, and engine speed are in a relationship that does not cause a shift shock, a control device (not shown) controls the side where the corresponding one-way clutch is not interposed. clutch K
1, K2, K3 and brakes B1, B2, and B3 are applied to completely connect or fix the parts.

[Effects of the Invention] As described above, according to the planetary gear type multi-stage transmission according to the present invention, multi-stage shifting of five or more stages is possible with a two-stage gear train, and the multi-stage transmission can be configured in a compact size. It is.

l6

[Brief explanation of drawings]

Fig. 1 is a schematic structural diagram of a planetary gear type multi-stage transmission according to the present invention, Fig. 2 is its speed diagram, Fig. 3 is its clutch and brake operation diagram, and Fig. 4 is a schematic diagram of another embodiment. composition,
FIG. 5 is a diagram of the clutch and brake operation. 1...First gear train (first gear train) IS...Sun gear 1P...Planetary gear IC・
...Carrier (planetary gear holding member) 2...Second gear train (second gear train) 2S...Sun gear 2C...Carrier (planetary gear holding member) 21F, 2
2F... Planet gear 10... Input shaft 31... First connecting member 32... Second connecting member

Claims (1)

[Scope of Claims] A first gear train in which one planetary gear is meshed and interposed between a sun gear and a ring gear is provided on the outside of the input shaft, and a pair of planetary gears are meshed between the sun gear and the ring gear. An interposed second gear train is configured and arranged, and the planetary gear holding member of the first gear train and the sun gear of the second gear train are connected by a first connecting member, and the first gear train and a ring gear of the second gear train are connected by a second connecting member, and the input shaft and the sun gear of the first gear train, the first connecting member, and the second gear train are connected to each other by a second connecting member. planetary gear holding member,
A clutch mechanism is interposed between the two members to engage each other in a manner that prevents relative rotation, and the sun gear of the first gear train, the first connecting member, and the planetary gear of the second gear train A planetary gear type multi-stage transmission, characterized in that the holding member is provided with a respective braking mechanism capable of regulating rotation of the holding member, and the second connecting member is configured as an output shaft.