JPH02129447A - Planetary gear type transmission for vehicle - Google Patents

Abstract

PURPOSE:To reduce the size of a transmission by disposing the first double pinion type planetary gear and the second and third single pinion type planetary gears in order, and selectively operating the first to fourth clutches and the first to third brakes. CONSTITUTION:The first double pinion type planetary gear 16 and the second and third single pinion type planetary gears 18, 10 are disposed on the same axis as input and output shafts 14, 22. The input shaft 14 is connected through a clutch K1 to the third ring gear 20r, through K2 to the third sun gear 20s, further through K4 to the second carrier 18c and the first ring gear 16r, and through K3 to the first and second sun gears 16s, 18s. The first speed is obtained by the operation of the clutches K1, K3 and a brake B1, similarly the second speed by K1, K3, B2, the third speed by K1, K2, B3, the fourth speed by K1, K2, K3, the fifth speed by K2, K4, B3, and the backward gear stages are obtained by K2, K3 and B2. Thus, input torque is transmitted directly to the third ring gear at a low speed gear stage with large torque, so that it is advantageous in strength, and a transmission can be reduced in size.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to an improvement in a planetary gear transmission provided between a prime mover and a drive wheel in a vehicle such as an automobile or a railway vehicle.

BACKGROUND OF THE INVENTION In conventional technical vehicles, play gear type transmissions suitable for automatically selecting a plurality of predetermined transmission gears are often used. Such a planetary gear type transmission is desired to be simple and compact, to be able to have a wide range of gear ratios, and to be easy to control gear changes.

On the other hand, for example, JP-A-51-17767, JP-A-51-48062, JP-A-51-108,
As described in JP-A No. 168 and JP-A-51-108170 as the first embodiment, two single pinion type planetary gear units and one double pinion type planetary gear unit are connected in series. An array of planetary gear transmissions for vehicles has been proposed. According to this, the structure is relatively simple, and five forward gears are provided, so that a wide gear ratio range can be ensured.

Problems to be Solved by the Invention However, in such conventional transmission devices, in a low speed gear stage where a large transmission ratio (rotational speed of input member/rotational speed of output member) is required to transmit a large torque, the input member is Since it is connected to the sun gear, it is necessary to increase the size of the sun gear from the standpoint of strength design, which poses a problem in that the outer diameter of the transmission becomes large. A transmission in which the input member is connected to a ring gear has also been considered, but the gear ratio ρ (number of teeth of the sun gear/number of teeth of the ring gear) of the planetary gear unit is inappropriate, and the outer diameter of the transmission is also Each element of the planetary gear system becomes larger,
i.e. Sanghya or Carrier.

This was not always satisfactory, as the rotation speeds of the planetary gears and ring gears increased, causing problems with the durability of bearings, etc.

The present invention was made against the background of the above circumstances, and its purpose is to maintain the gear ratio ρ of the planetary gear system and the rotational speed of each element within an appropriate range, and to The object of the present invention is to enable power transmission by connecting a member to a ring gear.

Means for Solving the Problems To achieve the objects, the present invention provides: (a) a first sun gear, at least a pair of first planetary gears meshing with each other and one of which meshes with the first sun gear; A double-binion type first planetary gear device including a first ring gear that meshes with the other gear, and a first carrier that rotatably supports the first planetary gear, and (c) a second sun gear that meshes with the second sun gear. (C) a second planetary gear device of a single pinion type, comprising a second planetary gear, a second ring gear that meshes with the second planetary gear, and a second carrier that rotatably supports the second planetary gear; A single pinion type third planetary gear comprising a sun gear, a third planetary gear that meshes with the third sun gear, a third ring gear that meshes with the third planetary gear, and a third carrier that rotatably supports the third planetary gear. In a planetary gear transmission for a vehicle, the devices are sequentially provided on the same axis, and the rotation of the input member is changed in stages and transmitted to the output member, wherein (d) the first sun gear and the second sun gear; (e) selecting the third ring gear as the input member; a first engagement device that selectively couples the third sun gear to its input member; and a second engagement device that selectively couples the first sun gear and the second sun gear to the third sun gear. a third engagement device that connects the first ring gear and the second carrier to the third engagement device;
a fourth engagement device selectively connected to the sun gear;
a fifth engagement device that selectively couples the carrier to the position fixing member; a sixth engagement device that selectively couples the first ring gear and the second carrier to the position fixation member; and the first sun gear and the second engagement device. A seventh engagement device for selectively connecting the sun gear to the position fixing member is provided.

The above-mentioned seven engagement devices selectively connect the respective elements, that is, disengage them as appropriate, and include multi-disc or band-type clutches, brakes,
It may be appropriately configured with a one-way clutch or a combination thereof. Furthermore, each engagement device may not only be configured independently, but also a plurality of engagement devices may be configured as a single product having multiple functions.

In a planetary gear transmission for a vehicle that requires a lot of action, the first
．． Third. and a fifth engagement device, the input member and the third
Between the ring gear and the 1st. When the second sun gear and the third sun gear are connected simultaneously, and the first carrier and the position fixing member are connected at the same time, the first gear stage with the largest transmission ratio is obtained. 1st, 3rd. and the sixth mooring device between the manpower member and the third ring gear. When the second sun gear and the third sun gear are connected simultaneously, and the first ring gear and the second carrier are connected to the position fixing member at the same time, the second speed gear has a smaller gear ratio than the first speed gear. is obtained. 1st. Third. and a seventh engagement device between the input member and the third ring gear. between the second sun gear and the third sun gear; When the second sun gear and the position fixing member are connected at the same time, a third gear with a smaller gear ratio than the second gear is obtained.

1st. Second. When the third mooring device simultaneously connects between the input member and the third ring gear, between the input member and the third sun gear, and between the first sun gear, the second sun gear, and the third sun gear. , a fourth gear with a smaller gear ratio (-1, O) than the third gear is obtained.

Second. 4th. and the seventh engagement device between the input member and the third sun gear, between the third sun gear and the first ring gear and the second carrier, and between the first. When the second sun gear and the position fixing member are connected at the same time, a fifth gear with a smaller gear ratio than the fourth gear is obtained. Also, the second. Third. And the sixth engagement device simultaneously connects between the input member and the third sun gear, between the first and second sun gears and the third sun gear, and between the first ring gear and second carrier and the position fixing member. When connected, a reverse gear is obtained.

Note that the fourth gear stage can also be established by simply connecting the input member and the third ring gear and the input member and the third sun gear simultaneously using the first and second engagement devices. obtain. Also, 1st degree, 2nd degree. In addition to or in place of the third engagement device, a fourth engagement device may be used to connect the third sun gear, first ring gear, and second carrier.

EXAMPLE Hereinafter, an example of the present invention will be described in detail based on the drawings.

FIG. 1 is a schematic diagram of a planetary gear type transmission for a vehicle, which is an embodiment of the present invention. Input shafts 14 arranged sequentially on a common axis within the case 12. First planetary gear device 16
．． Second planetary gear unit 18. Third planetary gear device 20. and an output shaft 22. The input shaft 14 is connected to the engine 26 of the vehicle via a torque converter 24, and the output shaft 22 is connected to the drive wheels of the vehicle via a differential gear device (not shown). The input shaft 14 and the output shaft 22 correspond to an input member and an output member, respectively. In addition, Transmitushiran case 12
corresponds to the position fixing member. Note that since the transmission 10 and the torque converter 24 are configured line-symmetrically with respect to the axis, the lower side of the axis is omitted in the skeleton diagram of FIG. 1.

The first planetary gear device 16 is a well-known double pinion type planetary gear device, and includes a first sun gear 16s,
at least a pair of first planetary gears 16p that mesh with each other;
It includes a first carrier 16c and a first ring gear 16r, and at least a pair of first planetary gears 16p rotatably supported by the first carrier 16c are located between the first sun gear 16S and the first ring gear 16r. One of the pair of first planetary gears 16p is the first sun gear 16.
s, and the other is engaged with the first ring gear 16''.

On the other hand, the second planetary gear device 18 and the third planetary gear device 2
0 is a single pinion type planetary gear device, and the second planetary gear device 18 includes a second sun gear 18s, a second planetary gear 18p, a second carrier 18c, and a second ring gear 18r. A second planetary gear 18p rotatably supported by a carrier 18c is located between a second sun gear 18s and a second ring gear 18r and meshes with them. In addition, the third planetary gear device 2
0 is the third sun gear 20s, the third planetary gear 20p, the third
The third planetary gear 20p, which includes a carrier 20c and a third ring gear 2Or, is rotatably supported by the third carrier 20c, and is located between the third sun gear 20s and the third ring gear 20r and meshes with them. has been done.

Further, the transmission 10 has a first sun gear 16s.
and second sun gear 18s are integrally connected to each other, first ring gear 16r and second carrier 18c are integrally connected to each other, and second ring gear 18r, third carrier 20c, and output shaft 22 are integrally connected to each other. is connected to. 1 to a first clutch that selectively connects a third ring gear 2Or to the input shaft 14, and a third sun gear 20.
2 to a second clutch that selectively connects S to the input shaft 14, and connects the first sun gear 16s and second sun gear 18s to the third clutch.
3 to a third clutch that selectively connects the sun gear 20s, and 4 to a fourth clutch that selectively connects the first ring gear 16r and the second carrier 18c to the third sun gear 20s.
and the first carrier 16c is attached to the transmission case 1.
2, a second brake B2 that selectively connects the first ring gear 16r and the second carrier 18c to the transmission case 12, and the first sun gear 16s and the second sun gear 18s. A third brake B3 selectively connected to the transmission case 12 is provided.

2 to the first clutch Kl and the second clutch. 3 on the third clutch. 4 on the 4th clutch. First brake Bl, second brake B2. The third brake B3 is operated by a hydraulic actuator of a type commonly used in conventional automatic transmissions for vehicles, such as a multi-plate clutch or one band or two bands wound in opposite directions. It is composed of a band brake, etc., or a one-way clutch, etc. Also, between the first clutch 1 and the input shaft 14.degree. and the third ring gear 20r, and the second clutch 2 and the input shaft 14.degree. between the third sun gear 20s, between the third clutch and the third sun gear 20S, between the first sun gear 16S and the second sun gear 18s, between the fourth clutch and the third sun gear 20
A connecting member may be provided between the second carrier 18c and the second carrier 18c as necessary. Similarly, between the first brake Bl and the first carrier 16c, between the second brake B2, the first ring gear 16r, and the second carrier 18c, and between the third brake B3 and the first sun gear 16s, and the second sun gear 18s. or between each element constituting each planetary gear device 16, 18, 20, the second ring gear 18r, the third carrier 2
In this embodiment, a connecting member may be interposed between the first clutch Kl and the output shaft 22 as needed.

2 on the second clutch. 3 on the third clutch. 4 on the 4th clutch. The first brake Bl, the second brake B2, and the third brake B3 are the first engagement device, the second engagement device, the third engagement device, the fourth engagement device, and the fifth engagement device.

They correspond to the sixth engagement device and the seventh engagement device, respectively.

In the transmission 10 configured as above, for example,
As shown in the operating state by mark Q in FIG. 2, the first clutch Kl and the second clutch 2. 3 on the third clutch. 4° to the 4th clutch. 1st brake Bl, 2nd brake B2. By respectively operating the third brake B3, a desired speed change gear from five forward speeds and one reverse speed is established. In FIG. 2, the gear ratio ρ1 of the first planetary gear unit 16 is 0.205, the gear ratio ρ2 of the second planetary gear unit 18 is 0.429, and the gear ratio ρ of the third planetary gear unit 20 is 0. The speed ratio (rotational speed of input shaft 14/rotational speed of output shaft 22) of each speed change gear in the case of 300 is shown. This is the rotation speed Nl of the ring gear in the double pinion type first planetary gear device 16.
, carrier rotation speed Nc, and sun gear rotation speed N,
is expressed by the following equation (1), where the gear ratio is ρ. On the other hand, the second planetary gear device 18. The rotation speed N of the ring gear in the third planetary gear device 20.

The rotational speed Nc of the carrier and the rotational speed N of the sun gear are expressed by the following equation (2), where ρ is the gear ratio, and are determined based on the equations (1) and (2). In addition,
The number of teeth of the first sun gear 16s is Z I 1 + the number of teeth of the first ring gear 16r is Z I F + the first second sun gear 18
The number of teeth of s is Z□, and the number of teeth of second ring gear 18r is Ztl.
, the number of teeth of the third sun gear 20s is Z. , third ring gear 2
If the number of teeth at 0r is Zl, then the gear ratio ρ is Z,...
/Z,... Gear ratio ρ2 is Z t-/Z t-, gear ratio ρ is Z. /2. , is.

N*-(1-ρ)NC+ρN, ...(1)N*
-(1+ρ)Nc-ρN, (2) The operation of each transmission gear will be explained below.

First, in the case of the first gear, the first clutch Kl and the third clutch are connected to 3. By activating the first brake B1, there are
c and the transmission case 12 are connected. Thereby, the power input to the input shaft 14 is transmitted to the third ring gear 2Or, and then to the first sun gear 16S.

The first ring gear 16r, the second sun gear 18s, the second carrier 18C2, and the third sun gear 20s are rotated in the opposite rotation direction with respect to the input shaft 14, while the second ring gear 18r, the third carrier 20C1, and the third ring gear 20r are It is rotated in the same direction as the input shaft 14. As a result, the second ring gear 18r and the third carrier 20c
The output shaft 22 connected to the input shaft 14 is rotated at a reduced speed in the same positive rotation direction as the input shaft 14 at a gear ratio of 3.5.

In the case of the second gear, the first clutch Kl.

3 on the third clutch. By operating the second brake B2, the input shaft 14 and the third ring gear 2Or
between the first sun gear 16s and the second sun gear 18s
and third sun gear 20s, and between first ring gear 16r and second carrier 18c and transmission case 12. As a result, input shaft 1
4 is transmitted to the third ring gear 2Or, and the first sun gear 16S, second sun gear 18S, and third sun gear 20s are rotated in the opposite rotation direction with respect to the input shaft 14, while the first carrier 16C5 The second ring gear 18r, the third carrier 20C9, and the third ring gear 20r are rotated in the same direction as the input shaft 14. As a result, the second ring gear 18r and the third carrier 20c
The output shaft 22 connected to the input shaft 14 is rotated at a reduced speed in the same positive rotation direction as the input shaft 14 at a gear ratio of 2.0.

In the case of the third gear, the first clutch Kl.

3 on the third clutch. By operating the third brake B3, the input shaft 14 and the third ring gear 2Or
between the first sun gear 16s and the second sun gear 18s
and the third sun gear 20s, and the first sun gear 1
6s and second sun gear 18s and the transmission case 12 are connected. As a result, the input shaft 14
The power input to is transmitted to the third ring gear 2Or,
First carrier 16C9, first ring gear 16r, second carrier 18c, second ring gear 18r, third carrier 20
c and the third ring gear 2Or are rotated in the same direction as the input shaft 14. As a result, the second ring gear 18r
and the output shaft 22 connected to the third carrier 20c,
The input shaft 14 is rotated at a reduced speed in the same positive rotation direction at a gear ratio of 1.3.

In the case of the fourth gear, the first clutch Kl.

2 on the second clutch. By operating the third clutch 3, the input shaft 14 and the third ring gear 2Or
, between the input shaft 14 and the third sun gear 20s, and between the first sun gear 16s and the second sun gear 18s and the third sun gear 20s. As a result, the third sun gear 20s and the third carrier 20c of the third planetary gear device 20.

The third ring gear 20r is rotated together with the input shaft 14, and the power input to the input shaft 14 is directly transmitted to the output shaft 22. Therefore, the output shaft 22 is rotated in the same positive rotation direction as the input shaft 14 at a gear ratio of 1.0.

In the case of 5th gear, 2 degrees on the second clutch and 4 degrees on the fourth clutch. By activating the third brake B3, there are 2 sun gear 18g and transmission case 12
are connected. Thereby, the power input to the input shaft 14 is transmitted to the second carrier 18c, the first carrier 16C1, the first ring gear 16r, the second carrier 18c
, the second ring gear 18r, the third sun gear 20S, the third carrier 20c, and the third ring gear 2Or are connected to the input shaft 1.
It is rotated in the same direction as 4. As a result, the output shaft 22 connected to the second ring gear 18r and the third carrier 20c is rotated at an increased speed in the same positive rotation direction with respect to the human power shaft 14 at a gear ratio of 0.7.

In addition, in the case of reverse gear, the second clutch is
3. to clutch. When the second brake B2 is operated, a gap between the input shaft 14 and the third sun gear 20s, the first sun gear 16s, the second sun gear 18s, and the third
between the sun gear 20s and the first ring gear 16r
And the second carrier 18c and the transmission case 12 are connected. Thereby, the power input to the input shaft 14 is transmitted to the second sun gear 18s, and the first sun gear 16s, second sun gear 18s, and third sun gear 20s are rotated in the same direction as the input shaft 14, while the first sun gear 18s is rotated in the same direction as the input shaft 14. Carrier 16C, second ring gear 18r, third
The carrier 20c and the third ring gear 20r are rotated in the opposite rotation direction with respect to the input shaft 14. As a result,
The output shaft 22 connected to the second ring gear 18r and the third carrier 20c is rotated in a direction opposite to the input shaft 14 and rotated at a reduced speed at a gear ratio of 2.33.

Here, in the transmission 10 of the present embodiment, the first gear is the one that needs to transmit a large torque.

In the second gear and the third gear, the power input to the input shaft 14 is transmitted to the third ring gear 2Or. Therefore, compared to the case where the transmission is transmitted to the sun gear, it is advantageous in terms of strength, and the transmission device IO can be configured to be compact.

Furthermore, since the gear ratio ρ of each planetary gear device 16, 18.20 is within the range of 0.2 to 0.6, the outer diameter of the transmission 10 is particularly large in this respect as well. In addition, each sun gear 16s, 18 of the planetary gear device 16, 18° 20 when the rotation speed of the input shaft 14 is 1.
s, 20s, carriers 16c, 18c, 20c, ring gear 16r.

18r, 2Or, and planetary gears 16p, 18p.

As shown in Table 1, the rotation speed of 20p is relatively low (2.500 of the second planetary gear 18P in the first gear is the maximum), and the durability of the bearing etc. There is no harm to it. In addition, '1sJ, r2nd', r3rdJ, r4thJ, '5 in Table 1
tJ and rRev" respectively represent a first gear, a second gear, a third gear, a fourth gear, a fifth gear, and a reverse gear.

In addition, in the transmission w, 10 of this embodiment, the three clutches Kl, 2. 3, and 3 brakes Bl,
B2. Since B3 is concentrated on the engine side end of the transmission, the diameter of the non-engine side end of the transmission is reduced, while the hydraulic circuit is shortened, reducing piping loss and the space occupied by the hydraulic circuit. There are some advantages.

Furthermore, in the transmission 10 of this embodiment, the output shaft 22
is located at one end of the transmission on the non-engine side, and has a structure that allows direct connection to the propeller shaft, so it is suitable for use in FR vehicles, but by replacing the output shaft 22 with an output gear. , F.F.
It can also be easily used in vehicles. A transmission 30 shown in FIG. 3 is an example of this, in which an output gear 28 is used instead of the output shaft 22, and an engine 26 and a torque converter 24 are disposed on the output gear 28 side.

In this way, the differential gear device 32 and the output gear 28 can be located close to each other, so the output gear 28
There is an advantage that a long counter shaft provided parallel to the axis of the transmission 30 is not required in order to transmit power from the transmission to the differential gear 32. In addition, 34 is a counter east force for making the rotation direction the same direction.

Although one embodiment of the present invention has been described above in detail based on the drawings, the present invention can also be implemented in eleven other ways.

For example, in the above embodiment, the fourth gear is the first clutch K.
l, 2 to the second clutch. and is established by simultaneous connection of 3 to the third clutch, but 1 to the 1st clutch.
And only 2 on the second clutch, or 2 on the first clutch Kl and 2 on the second clutch. In addition to or instead of 3 to the third clutch, 4 may be connected to the fourth clutch.

Furthermore, although the torque converter 24 is used in the above embodiment, a torque converter with a lock-up clutch, a fluid coupling, a magnetic powder type electromagnetic clutch, a multi-disc or single-disc friction clutch, or the like may be used instead.

Further, each planetary gear device 16°18.
20 gear ratio ρ1. ρ8. Of course, it is possible to change ρ and the speed ratio of each gear.

Furthermore, the three clutches Kl in the embodiment.

K2. 3, and the three brakes B1, B2 and B3 are arranged centrally, respectively, but they do not necessarily need to be centrally arranged, and may be arranged separately depending on the arrangement conditions in the engine room.

Further, in the above embodiment, between the first sun gear 16s and the second sun gear 18s, between the first ring gear 16r and the second carrier 18c, and between the second ring gear 18r and the third carrier 2.
0c are each integrally connected, but each can be connected and disconnected by a clutch or the like.

Although other examples are not provided, the present invention can be implemented with various modifications and improvements based on the knowledge of those skilled in the art.

Effects of the Invention As detailed above, in the vehicular planetary gear transmission of the present invention, the power input to the input shaft is transmitted to the third ring gear in the low speed gear where large torque needs to be transmitted. This is advantageous in terms of strength compared to the case where the signal is transmitted to the sun gear, and the device can be made smaller.

Moreover, since the gear ratio of each planetary gear unit can be maintained within an appropriate range, the outer diameter of the transmission does not increase in this respect, and the sun gear, carrier, ring gear, and planetary gear of each planetary gear unit Since the rotation speeds of both can be maintained at relatively low rotation speeds, the durability of the bearings etc. is not impaired.

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram of a planetary gear type transmission for a vehicle, which is an embodiment of the present invention. FIG. 2 is a chart showing the relationship between the transmission gears of the embodiment shown in FIG. 1 and the engagement devices necessary to establish them. FIG. 3 is a schematic diagram showing another embodiment of the present invention. 10.30: Planetary gear type transmission for vehicles 12: Transmission case (position fixing member) 14: Input shaft (input member) 16: First planetary gear unit 18: Second planetary gear unit 20: Third planetary gear Device 22: Output shaft (output member) 28: Output gear (output member) 16s: First sun gear 16P: First planetary gear 16C
: 1st carrier 16r: 1st ring gear 18s: 2nd
Sun gear 18p: Second planetary gear 18c: Second carrier 18r: Second ring gear 20S: Third sun gear 20
p: Third planetary gear 20c: Third carrier 20r: Third
To the ring gear: 1: First clutch (first engagement device) K2: Second clutch (second engagement device W) Kl Third clutch (third engagement device) K4: Fourth clutch (fourth engagement device) B1: First brake (fifth engagement device) B2: Second brake (sixth engagement device) B3: Third brake (seventh engagement device) Applicant: Toyota Motor Corporation Figure 2

Claims (1)

[Scope of Claims] A first sun gear, at least a pair of first planetary gears that mesh with each other and one of which meshes with the first sun gear, a first ring gear that meshes with the other of the first planetary gears, and rotates the first planetary gear. a first planetary gear set of double pinion type with a first carrier capable of supporting a second sun gear; a second planetary gear meshing with the second sun gear;
a single pinion type second planetary gear device including a second ring gear meshing with a planetary gear and a second carrier rotatably supporting the second planetary gear; a third sun gear;
a single pinion type third planetary gear device comprising a third planetary gear that meshes with the third sun gear, a third ring gear that meshes with the third planetary gear, and a third carrier that rotatably supports the third planetary gear; are sequentially provided on the same axis, and the first sun gear and the second sun gear are connected to each other in a planetary gear transmission for a vehicle of the type that changes the rotation of the input member in stages and transmits the rotation to the output member, a first engagement that connects the first ring gear and the second carrier to each other, connects the second ring gear, the third carrier, and the output member to each other, and selectively connects the third ring gear to the input member; a second engagement device that selectively couples the third sun gear to the input member; a third engagement device that selectively couples the first sun gear and the second sun gear to the third sun gear; a fourth engagement device that selectively connects the first ring gear and the second carrier to the third sun gear; a fifth engagement device that selectively connects the first carrier to the position fixing member; a sixth engagement device that selectively connects the ring gear and the second carrier to the position fixing member;
A planetary gear type transmission for a vehicle, comprising: a seventh engagement device that selectively connects the first sun gear and the second sun gear to a position fixing member.