JPH0235246A - Planetary geared transmission for vehicle - Google Patents

Abstract

PURPOSE:To facilitate speed change control by combining No.1-No.2 planetary gearing devices of single pinion type selectively with No.3 planetary gearing device of double pinion type using No.1-No.3 clutches and brakes. CONSTITUTION:No.1-No.3 planetary gearing devices 16, 18, 20 couple together a carrier 16c and a ring gear 18r and also a sun gear 20s, carriers 18c and 20c, and speed change between an input shaft 14 and an output shaft 22 is made by selectively engaging clutches C1-C3 and brakes B1-B3. The 1st speed (gear ratio 3.0) is obtained by engagement of clutches C1, C3 and brake B1, the 2nd (2.2) by engagement of C1, C3, B2, the 3rd speed (1.3) by engagement of C1, C3, B3, and 4th speed (1.0) by C1-C3, the 5th speed (0.75) by C2, C4, B3, and the back position (3.0) by C2, C3, B2. Thus a wide range of gear ratio is obtained, and no input changeover is required at the time of shifting the gear position, and there is no risk of exclusive enlargement of the revolving speed of No.3 planet gear to result in enhancement of its durability.

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.

In prior art vehicles, planetary gear transmissions are often used, which are suitable for automatically selecting a plurality of predetermined gears. Such a planetary gear type transmission is desired to be simple and compact, to be able to have a large shift range, and to be able to easily control the speed change.

To solve this problem, a vehicle drifting M gear type transmission device is proposed, for example, as described in Japanese Unexamined Patent Publication No. 50-72066. According to this, the first Zangi...
a first carrier rotatably supporting a planetary gear, a single pinion type first planetary gear device including a first ring gear, a second sun gear, and a second sun gear rotatably supporting at least a pair of mutually meshing second planetary gears. a double pinion type second planetary gear device including two carriers and a second ring gear; a single pinion type third planetary gear device including a third sun gear and a third carrier rotatably supporting the third planetary gear; and a third ring gear; Because the planetary gears are arranged in series, it is simple and compact, provides 5 forward gears and a relatively wide speed ratio range, and when changing gears, the power input up to that point is reduced. This eliminates the need for so-called input switching, in which a path is disconnected and the next power input path is connected at the same time, and engine revs and planetary gear locks are eliminated, making gear change control easier.

Problems to be Solved by the Invention However, in the above-mentioned transmission, the number of rotations of the second planetary gear provided in the double pinion type second planetary gear device is significantly higher than that of other components. Therefore, there is a problem in that the eyes of the second planetary gear wear out relatively quickly, which impairs the durability of the entire device.

The present invention has been made against the background of the above circumstances, and its purpose is to provide a system in which a 2 Mi single pinion type planetary gear unit and a set of double pinion type planetary gear units are arranged. An object of the present invention is to provide a planetary gear type transmission for a vehicle, which provides five forward gears and a wide range of gear ratios, facilitates speed change control, and has suitable durability.

Means for Solving the Problems In order to achieve the object, the gist of the present invention is to provide a single pinion type device having a first sun gear, a first carrier rotatably supporting a first planetary gear, and a first ring gear. The first planetary gear device, the second gear, the second gear
A second carrier rotatably supports a tl star gear, a single pinion type 2'tl star gear device including a second ring gear, a third sun gear, and at least one pair of mutually meshing third planetary gears. A third career,
A vehicular planetary gear type in which a double pinion type third planetary gear unit equipped with a third ring gear is sequentially installed on the same axis, and the rotation of the input member is shifted in stages and transmitted to the output system. In the transmission, (a) the first carrier, the second ring gear, the third sun gear, and the output section +1 are connected to each other, and the second carrier and the third carrier are connected to each other; a second engagement device that selectively couples the first sun gear to the input member; a second engagement device that selectively couples the first sun gear to the input member; and a second engagement device that selectively couples the first sun gear to the input member; a third engagement device selectively coupled to the second carrier; a fourth engagement device selectively coupled the first sun gear to the second carrier; and a fifth engagement device selectively coupled the third ring gear to the position fixing member. an engagement device, a sixth engagement device for selectively coupling the third carrier to the position fixing member, and a seventh engagement device for selectively coupling the second sun gear to the position fixation member; That's true.

Effect If you do this, the first thing. When the input member and the first ring gear, the first sun gear and the second sun gear, and the third ring gear and the position fixing member are simultaneously connected by the third and fifth engagement devices, the most A first gear with a large transmission ratio can be obtained. 1st. between the input member and the first ring gear by the third and sixth engagement devices;
When the sun gear and the second sun gear and the third carrier and the position fixing member are simultaneously connected, a second speed gear with a smaller gear ratio than the first speed gear is obtained. 1st
．． Third. and a seventh engagement device, the input member and the first
When the ring gear, the first sun gear and the second sun gear, and the second sun gear and the position fixing member are connected at the same time, the third gear has a smaller gear ratio than the second gear. is obtained. by the first and second engagement devices;
When the input member and the first ring gear and the input member and the first sun gear are connected simultaneously, or the first
．． When the input member and the first ring gear, the input member and the first sun gear, and the first lean gear and the second sun gear are simultaneously connected by the second and third engagement devices, the third engagement device Gear ratio smaller than the higher gear (-1,0)
4th gear stage is obtained. Second. When the input member and the first sun gear, the first sun gear and the second carrier, and the second sun gear and the position fixing member are simultaneously connected by the fourth and seventh engagement devices, the A fifth gear with a smaller gear ratio than the fourth gear is obtained. Also,
Second. When the input member and the first sun gear, the first Zang gear and the second sun gear, and the third carrier and the position fixing member are simultaneously connected by the third and sixth engagement devices, the reverse movement The gear stage is obtained.

Effects of the Invention As described above, according to the present invention, selective actuation of the engagement device enables the previous ii! i5 gears and a wide range of gear ratios are obtained, and so-called input switching is not required when changing gears. Moreover, according to the present invention, the rotational speed of the third planetary gear in the double pinion type 3M star gear device does not increase significantly, and the rotation speed of the third planetary gear does not increase significantly.
Since only the planetary gear does not wear out earlier than other components, the durability of the entire device is improved compared to conventional devices.

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

FIG. 1 is a schematic diagram showing the configuration of a vehicular planetary gear type transmission 10 (hereinafter simply referred to as transmission 10). In the figure, the transmission 1o includes an input shaft 14, a 1i star gear device 16, a 2nd star gear device 16, and a
It includes a planetary gear device 18, a third planetary gear device 20, and an output gear 22. The input shaft 14 is connected to the engine 26 of the vehicle via a torque converter 24, and the output gear 22 is connected to the drive wheels of the vehicle via a differential gear (not shown). In this embodiment, the input shaft 14 and the output gear 22 correspond to an input member and an output member, respectively. Also, i-Lance Mission Case 1
2 corresponds to a position fixing member. Note that, since the transmission 10 and the torque converter 24 are constructed 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 and the second planetary gear device 1
8 constitute a well-known single pinion type planetary gear device. In addition, the third planetary gear device 20
is a well-known double pinion type planetary gear system. The first planetary gear device 16 includes a first sun gear 16s, a first planetary gear 16p, a first carrier 16c, and a first ring gear 16r. The first planetary gear 16p is rotatably supported by the first carrier 16c. 1st sun gear 1
6s and the first ring gear 16r, and is meshed with them. Further, the second planetary gear device 18 includes a second sun gear 18s, a second planetary gear 18p, a second carrier 18c, a second ring gear 18r, and a second sun gear 18s.
A second planetary gear 18p rotatably supported by a carrier 18c is connected to a second sun gear 18s and a second ring gear 1.
It is located between and meshed with 8r.

The third planetary gear device 20 has a third sun gear 20s.
, a pair of third planetary gears 2゜p that mesh with each other, a third carrier 20c, and a third ring gear 2Or.
The third planetary gear 20p rotatably supported by the carrier 20c is connected to the third sun gear 20s and the third ring gear 2.
It is located between and interlocked with Or.

In the transmission 10, the first carrier 16c, the second ring gear 18r, the third lean gear 20S, and the output gear 22 are integrally connected, and the second carrier 18c and the third carrier 20c are integrally connected. ing.

A first clutch C1 selectively connects the first ring gear 16r to the input shaft 14, a second clutch C2 selectively connects the first sun gear 16s to the input shaft 14, and a first clutch C2 selectively connects the first sun gear 16s to the input shaft 14.
A third clutch C3 that selectively connects the sun gear 16s to the second sun gear 1.8 s, and a fourth clutch C that selectively connects the first zang gear 1.6 s to the second carrier 18C.
4, and a first brake B1 that selectively connects the third ring gear 2 Or to the transmission case 1 to the transmission case 12;
A second brake B2 that selectively connects the third carrier 20c to the transmission case 12, and a third brake B3 that selectively connects the second sun gear 18s to the I-transmission case 12 are provided. .

The first clutch CL, second clutch C2, third clutch C3, fourth clutch C4, first brake B1, second brake B2, and third brake B3 are often used in conventional automatic transmissions for vehicles. It is operated by a type of hydraulic actuator, and consists of a multi-disc clutch, one handbrake, or two handbrakes in opposite directions of the winding LJ force. Further, between the first brake B1 and the third ring gear 2Or, the second brake B2
and the third carrier 20c, and between the third brake gear B3 and the second sun gear 18s, a connecting member may be provided as necessary. Similarly, between the first clutch C1 and the first ring gear 16r, the second clutch C2 and the first Zangi
s, between the third clutch C3 and the first sun gear 16s and the second sun gear 18s, and between each planetary gear set 16.
Between each element constituting the 18° 20, the third sun gear 20s
A connecting member may be interposed between the output gear 22 and the output gear 22 as necessary. In this embodiment, the first crunch C
1, second clutch C2, third clutch C3, fourth clutch C/I, first brake B1, second brake B2, third
The brake B3 includes a first engagement device, a second engagement device, a third engagement device, a fourth engagement device, a fifth engagement device, a sixth engagement device,
and a seventh engagement device, respectively.

] 2 In the transmission 10 configured as above, for example,
As the operating states are indicated by the second circle, the first clutch CI, the second clutch C2, the third clutch C3, the fourth clutch C4, the first brake B1, the second brake B2, the third clutch By simultaneously operating three of the brakes B3 by hydraulic actuators, a desired gear stage is established, and one or two of the three engaging devices engages one or two of the other engaging devices. 5 forward speeds and 1 reverse speed
A gear shift may be performed. In FIG. 2, the gear ratio ρ of the first M planetary gear device 16 is 0°3, and the second planetary gear device 1
8, the gear ratio ρ2 of the third ffiffi gear device 20 is 0.333, and the gear ratio ρ3 of the third ffiffi gear device 20 is 0.4. has been done. In addition, the number of teeth of the first sun gear 16s is Z I S % The number of teeth of the first ring gear 6r is Z
l r %The number of teeth of the first sun gear 16s is 22s, the second
The number of teeth of the ring gear 18r is Z2r, and the third sun gear is 20s.
When the number of teeth of the third ring gear is Z3s and the number of teeth of the third ring gear is Z3r, the gear ratio ρ is Z+-/Z+r, and the gear ratio ρ2 is Z2. , /Z2r.

Gear ratio ρ1 is Z3-/23. It is.

That is, in the transmission 10 of this embodiment, the first clutch CI, the third clutch C3, and the first brake B1
Accordingly, between the input shaft 14 and the first ring gear 1.6r, between the first sun gear 16s and the second sun gear 18s,
When the third ring gear 20r and the I-transmission engine case 12 are connected simultaneously, the first gear with the largest gear ratio is obtained, and the output gear 22 is connected to the gear ratio r.
3. It is rotated in the same direction as the input shaft 14 by OJ.

In addition, the first clutch C1, the third clutch C3 and the second clutch
The input shaft 14 and the first ring gear 1 are rotated by the brake B2.
6r, first sun gear 16s and second sun gear 18s
When the third carrier 20c and the transmission case 12 are simultaneously connected, a second gear with a smaller gear ratio than the first gear is obtained, and the output gear 22 is connected with the gear ratio r. 2.2 Rotated in the same direction as the input shaft 14 at J.

In addition, the first clutch CI, the third clutch C3 and the third clutch
By the brake B3, the input shaft 14 and the first ring gear 1
Between 6r and 1st sun gear 16S and 2nd sun gear],
8s and the second sun gear 18s and the transmission case 12 are simultaneously connected, the second sun gear 18s and the transmission case 12 are connected simultaneously.
A third gear with a smaller gear ratio than the second gear is obtained,
The output gear 22 is rotated in the same direction as the input shaft 4 at a gear ratio r 1.3.

Also, the first clutch CI, the second clutch C2 and the third clutch
By the crunch C3, the human power shaft 14 and the first ring gear +
16r, between the human power shaft 14 and the first sun gear 16s, and between the first sun gear 16S and the second sun gear 18s, the first gear with a smaller gear ratio than the third gear. A fourth gear is obtained, and the output gear 22 is rotated in the same direction as the input shaft 14 at a gear ratio r ], OJ.

Further, by the second clutch C2, the fourth clutch C4, and the third brake B3, the position between the input shaft 14 and the first sun gear 16s, the first sun gear 16s and the second carrier L8
When the transmission case 12 and the transmission case 12 are connected at the same time, a fifth gear with a smaller gear ratio than the fourth gear is obtained, and the output The gear 22 is connected to the input shaft 14 at a gear ratio ro of 75J.
rotated in the same direction.

The second sun gear 16s and the second sun gear 18 are connected between the human power shaft 14 and the first sun gear 16s by the second clutch C2, the third clutch C3, and the second brake B2.
When the third carrier 20c and the transmission case 12 are simultaneously connected, a reverse gear stage is obtained, and the output gear 22 is connected to the gear ratio r3.s. It is rotated in the opposite direction to the input shaft 14 by the OJ.

Here, in the above-mentioned speed change control, as shown in Table 1 below, the rotation speed of the third planetary gear 20p in the third planetary gear unit 20, which is a double pinion type, is relatively small at each gear stage. It has become clear from experiments conducted by the inventor that this is not a particularly large value even when compared with the rotation speed of other components. This is the case where the input rotation speed is set to 14 rotations.On the other hand, the double pinion type transmission of the conventional transmission as described in the above-mentioned Japanese Patent Application Laid-Open No. 50-72066. As shown in Table 2, the rotational speed of the second planetary gear in the second planetary gear device is 3rd higher than the rotational speed of other components, assuming that the manual rotational speed is "1".
It can be seen that the values are significantly large except for the 5th and 4th gears.

As shown in Table 1 and Table 2, the planetary gear transmission 1 for a vehicle according to the present embodiment
0, the rotational speed of the third M star gear 20p of the third planetary gear unit 2o, which is a double pinion type, is made relatively small during speed change control, and the five forward gears are changed by selective operation of the engagement device. A wide gear ratio range can be obtained, and so-called input switching is not required when changing gears. Therefore, according to this embodiment, the rotational speed of the double pinion type planetary gear is higher than that of other gears. Since only the second planetary gear does not wear out prematurely due to the rotational speed of the component being too large, the durability of the entire device is improved compared to conventional devices. This effect can be obtained.

In the above embodiment, the fourth gear was established by the first clutch CI, the second clutch C2, and the third clutch C3, but instead of this, the first clutch C1 and the second clutch C3 established the fourth gear. There is no problem even if the fourth gear is established only by C2.

Further, in the above-mentioned embodiment, the torque converter 24 is used, but instead, a torque converter with a lock-up clutch, a fluid coupling, a magnetic particle type electromagnetic clutch, a multi-disc or single-disc friction clutch, etc. may be used. obtain.

The above-mentioned embodiment is merely one embodiment of the present invention, and various modifications may be made to the present invention without departing from the spirit thereof.

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram showing the main structure of a power transmission device including a vehicular planetary gear transmission according to 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. 10: Vehicle planetary gear type transmission 12 Nidoran transmission case (position fixing member) 14
; Input shaft (input member) 16: First planetary gear device 16S: First sun gear 16p: First planetary gear 16C: First carrier 16r: First ring gear 18: Second planetary gear 18s: Second sun gear 18p: Second Planetary gear 18c: Second carrier 18r: Second ring gear 20: Third planetary gear device 20s: Third sun gear 20p: Third planetary gear 20c: Third carrier 20r; Third ring gear 22: Output gear (output member) C1; First clutch (first engagement device) C2: Second clutch (second engagement device) C3; Third clutch (third engagement device) C4: Fourth clutch (fourth engagement device) B1: First Brake (fifth engagement device) B2: Second brake (sixth engagement device) B3: Third brake (seventh engagement device)

Claims (1)

[Claims] A first sun gear that rotatably supports a first planetary gear.
A single pinion type first planetary gear device including a carrier and a first ring gear, a second sun gear and a second carrier rotatably supporting the second planet gear, and a single pinion type second planetary gear including a second ring gear. A gear device, a third sun gear, a third carrier rotatably supporting at least one pair of mutually meshing third planetary gears, and a double pinion type third planetary gear device including a third ring gear are sequentially provided on the same axis. In a planetary gear transmission for a vehicle, which changes the rotation of an input member in stages and transmits the rotation to an output member, the first carrier, the second ring gear, the third sun gear, and the output member are connected to each other. , the second carrier and the third carrier
a first engagement device that selectively couples the first ring gear to the input member while coupling the first ring gear to the input member; and a second engagement device that selectively couples the first sun gear to the input member. a third engagement device that selectively connects the first sun gear to the second sun gear; and a third engagement device that selectively connects the first sun gear to the second sun gear.
a fourth engagement device selectively coupled to the carrier; and the third engagement device;
a fifth engagement device that selectively couples the ring gear to the position fixing member; a sixth engagement device that selectively couples the third carrier to the position fixing member; and a sixth engagement device that selectively couples the second sun gear to the position fixing member. A planetary gear type transmission for a vehicle, characterized in that a seventh engagement device for selective connection is provided.