JPH02146339A - Planet gear type transmission device for vehicle - Google Patents

Abstract

PURPOSE:To eliminate the necessity for selecting an input, when a low speed gear shift is selected, by placing in a normally connected condition or in a connectable condition by an engaging device respectively a relation between the first and second sun gears, between each of the first and second sun gear and the third ring gear, between the first carrier and the second ring gear and between the second and third carriers. CONSTITUTION:A device coaxially provides the first to third single pinion type planetary gears 16, 18, 20, mutually integrally connecting respectively an input shaft 14 and the first sun gear 16s, first carrier 16c and the second ring gear 18r, second sun gear 18s and the third ring gear 20r while the second carrier 18c, third carrier 20c and an output shaft 22. By operating the device respectively interposing the first to third clutches K1 to K3 and the first to third brakes B1 to B3, a desired speed change gear shift can be established among forward five speed shifts and reversing one speed shift. Thus because the necessity is eliminated for selecting an input when adjacent speed change gear shifts are selected, a speed change control is facilitated.

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 transmission gears. For example, Japanese Patent Publication No. 50-32913,
The planetary gear type transmission for a vehicle described in Japanese Patent Publication No. 51-3012 is one example of such a transmission, in which three sets of planetary gears are arranged in series. According to this, the structure is relatively simple, and five forward gears are provided, so that a wide gear ratio range can be ensured. Further, there is an advantage that the outer diameter of the transmission can be made relatively small as long as the gear ratio ρ (number of teeth of sun gear/number of teeth of ring gear) of each planetary gear device is within an appropriate range.

Problems to be Solved by the Invention However, in the conventional planetary gear transmission described above, when changing gears from second speed to third speed or from first speed to second speed, the power input path up to that point is Since so-called input switching is performed in which the next power input path is connected at the same time as the next power input path is disconnected, there is a drawback that control becomes delicate. In other words, if a blank period of power transmission occurs between disconnecting the previous power input path and connecting the next power input path, the engine will rev up, and conversely, when the input is switched, one of the power input paths will be released. If two engaging devices are engaged at the same time, the transmission will lock and the resulting shock will occur. Therefore, delicate switching control that prevents the engine from revving up and the transmission from locking is required. is required, making it difficult to stably perform smooth switching control.

In addition, such inconvenience is especially caused by low speed gear changes from 1st to 3rd gears, which have a large gear ratio (rotational speed of human-powered member/rotational speed of output member) where the gear change is performed in the high engine speed range. It becomes noticeable when

The present invention has been made against the background of the above-mentioned circumstances, and its object is to provide a planetary gear type transmission for a vehicle that does not require input switching particularly when changing a low speed gear.

Means for Solving the Problems To achieve the objects, the present invention provides (a) a first sun gear, a first planetary gear that meshes with the first sun gear, a first ring gear that meshes with the first planetary gear, and a single pinion type first planetary gear device including a first carrier rotatably supporting the first planetary gear; (b) a second planetary gear device;
a sun gear, a second planetary gear that meshes with the second sun gear;
(C) a single pinion type second planetary gear device including a second ring gear that meshes with the second planetary gear; and a second carrier that rotatably supports the second loose gear;
A third sun gear of a single pinion type, comprising a third 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 type transmission for a vehicle of a type in which a planetary gear unit is provided on the same axis and the rotation of an input member is shifted in stages and transmitted to an output member, the first sun gear, the second sun gear, and the A third ring gear, between the first carrier and the second ring gear, and between the second carrier and the third carrier can be connected at all times or by a locking device. shall be.

Embodiments Hereinafter, some embodiments of the present invention will be described in detail with reference to the drawings.

FIG. 1(a) is a schematic diagram of a planetary gear type transmission for a vehicle, which is an embodiment of the present invention. The input shafts 14 are sequentially arranged on a common axis in the transmission case 12 . First planetary gear device 16. Second planetary gear device 1B, third planetary gear device 20
．． and an output gear 22. The input shaft 14 is connected to a vehicle engine 26 via a torque converter 24, and the output gear 22 is connected to drive wheels of the vehicle via a differential gear device (not shown).

In this embodiment, the input shaft 14 and the output gear 22 correspond to an input member and an output member, respectively.

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(a).

Said first planetary gear device 16. The second planetary gear device 18 and the third planetary gear device 20 are respectively well-known single pinion type planetary gear devices, and the first planetary gear device 16 has a first sun gear 16s and a first planet gear t6p.
, a first carrier 16C2 and a first ring gear 16r, and a first planetary gear 16p rotatably supported by the first carrier 16c is connected to a first sun gear 16s and a first ring gear 16r.
It is located between and meshed with the ring gear 16r. The second W star gear device 18 is a second sun gear 18
s, a second planetary gear 1.8P, a second carrier 18c, and a second ring gear 18r.
The second planetary gear 18p rotatably supported by the second sun gear 18S and the second ring gear 18r is meshed with the second sun gear 18S and the second ring gear 18r. Further, the third planetary gear device 20 includes a third sun gear 20s, a third planetary gear 20
P, third carrier 20c, and third ring gear 2Or
A third planetary gear 20p rotatably supported by a third carrier 20c is located between and meshed with the third sun gear 20s and third ring gear 2Or.

In such a transmission 10, the input shaft 14 and the first sun gear 16s are integrally connected to each other, and the first carrier 16
c and the second ring gear 18r are integrally connected to each other, the second sun gear 18s and the third ring gear 20r are integrally connected to each other, and the second carrier 18c, the third carrier 20c, and the output gear 22 are integrally connected to each other. are connected. 1 to a first clutch that selectively connects the input shaft 14, the first sun gear 16s, the second sun gear 18s, and the third ring gear 2Or; 2 to the second clutch that selectively connects the ring gear 18r.
and a third clutch that selectively connects the input shaft 14, the first sun gear 16s, and the third sun gear 20s, and selectively connects the first carrier 16c and second ring gear 18r to the F transmission case 12. A first brake B1, a second brake B2 that selectively connects the first ring gear 16r to the transmission case 12, and a third brake B3 that selectively connects the third sun gear 20s to the transmission case 12 are provided. .

The first clutch Kl is an engagement device that enables connection between the first sun gear 16s, the second sun gear 18s, and the third ring gear 2Or.

2 to the first clutch Kl and the second clutch. 3 on the third 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. 1 to the first clutch and input shaft 14. 1st sun gear 16s
, the second sun gear 18s, the second clutch 2 and the input shaft 14. 1st sun gear 16s”, 1st carrier 16c
A connecting member may be provided between the third clutch 3 and the input shaft 14, the first sun gear 16s, and the third sun gear 20s as necessary. Similarly, the first brake B
1 and the first carrier 16c, the second ring gear 18r, between the second brake B2 and the first ring gear 16r, between the third brake B3 and the third sun gear 20s, or between each planetary gear device 16.18. Between each element constituting 20,
Second carrier 18c2 third carrier 20C and output gear 2
2, a connecting member may be interposed as necessary.

In the transmission 10 configured as above, for example,
As the operating state is indicated by the ○ marks (see Fig. 1), the first clutch Kl and the second clutch are connected to each other. 3 on the third clutch. First brake B1 second 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. 1(b), the gear ratio ρ1 of the first planetary gear unit 16 is 0.317, and the gear ratio ρ1 of the second planetary gear unit 18 is 0.317.
2 is 0.400 and the gear ratio ρ3 of the third planetary gear device 20 is 0.379. . Single-binion type first planetary gear device 16.
2nd J star gear device 1st, ring gear rotation speed Ng in the third planetary gear device 20, carrier rotation speed N6. The rotational speed N of the sun gear is expressed by the following equation (1), where ρ is the gear ratio. Therefore, the speed ratio of each of the above-mentioned transmission gears is determined based on the equation (1). Note that the number of teeth of the first sun gear 16s is Zl, the number of teeth of the first ring gear 16r is ZIPs, the number of teeth of the second sun gear 18s is Zl, and the number of teeth of the second sun gear 18s is Zl.
Ring gear 18r teeth, number Zl1, third sun gear 20
The number of teeth of s is 231, and the number of teeth of third ring gear 20r is Zl.
, then the gear ratio ρ is Z1m/Zll'', the gear ratio ρ2 is Z.Zl21, and the gear ratio ρ.

is Z, , /Z3r.

Ni = (1+9) Nc-ρNs ・--(1
) The operation of each transmission gear will be explained below.

First, in the case of the first gear, the input shaft 14, the first sun gear 16s, and the second sun gear 18s are operated by the first clutch and the first brake Bl.
and third ring gear 20r, and between first carrier 16c and second ring gear 18r and transmission case 12. As a result, the output gear 22 is rotated at a reduced speed with respect to the input shaft 14 in the same positive rotation direction at a speed ratio (1+ρ, )/ρ.

In the case of the second gear, the first clutch Kl and the second
By operating the brake B2, the input shaft 14
The first sun gear 16s, the second sun gear 18s, and the third ring gear 20r are connected, and the first ring gear 16r and the transmission case 12 are connected. As a result, the output gear 22 rotates in the same positive rotation direction with respect to the input shaft 14 at the gear ratio (1+ρ,)(1+ρ2)/(
It is rotated at a reduced speed at ρ2+ρ1 (1+ρ2)).

In the case of third gear, the first and third clutches
By operating the brake B3, the input shaft 14
and between the first sun gear 16s, the second sun gear 18s and the third ring gear 2Or, and between the third sun gear 2Or.
0s and the transmission case 12 are connected. As a result, the output gear 22 is rotated at a reduced speed in the same positive rotation direction with respect to the input shaft 14 at a speed ratio of 1+ρ3.

In the case of fourth gear, the first and second clutches are connected to the first clutch.
2 is actuated by the clutch, the input shaft 14
and between the first sun gear 16s, the second sun gear 18s, and the third ring gear 2Or, and between the input shaft 14, the first sun gear 16S, the first carrier 16c, and the second
The ring gear 18r is connected to the ring gear 18r. As a result, each planetary gear device 16, 18, 20 is rotated integrally with the input shaft 14, and the output gear 22 is rotated in the same positive rotation direction with respect to the input shaft 14 at a gear ratio of 1.

Note that the fourth gear can be established by operating at least two of the three clutches Kl, 2, and 3.

In the case of fifth gear, the second and third clutches
By operating the brake B3, the input shaft 14
and between the first sun gear 16s and the first carrier 16c and the second ring gear 18r, and between the third sun gear 2
0s and the transmission case 12 are connected. As a result, the output gear 22 is rotated at an increased speed in the same positive rotation direction as the input shaft 14 at a speed ratio of 1-ρ2ρ.

In the case of reverse gear, by operating the third clutch 3 and the second brake B2, a gap between the input shaft 14 and the first sun gear 16s and the third sun gear 20s is generated.
Also, the first ring gear 16r and the transmission case 12 are connected. As a result, output gear 2
2 is rotated in the opposite rotation direction with respect to the input shaft 14, and the gear ratio -[l-ρ, (ρ2+ρ, (1+ρ2)
)ko/ρ.

The rotation is decelerated at (ρ2+ρ, (1+ρ2)).

As described in detail above, according to the transmission 10 of this embodiment, three sets of single pinion type planetary gear devices 16, 18
．． 20 are arranged on a common axis, the structure is relatively simple, while the three clutches Kl,
2. 3 and three brakes Bl, B2. Selective operation of B3 provides 5 forward gears and a wide range of gear ratios, making it possible to achieve both high-speed driving and start/uphill performance. This eliminates the need to increase the engine speed, improving fuel efficiency and quietness.

Moreover, since input switching is not required when switching between adjacent transmission gears, the speed change control becomes simple and easy. In particular, in this embodiment, each gear is established by simultaneously operating two of the six clutches and brakes, and by stopping the operation of one of the six clutches and brakes, one of the other clutches and brakes is activated. Since it is possible to change gears simply by operating the , speed change control becomes even easier.

Further, according to the transmission 10 of the present embodiment, the gear ratios ρ1. While maintaining ρ2゜ρ within an appropriate range, the gear ratios of the first to fourth gears are changed based on the characteristics of the engine 26 for each gear of the vehicle stepped transmission. Since the ratio is set to a value close to a desired geometric series, excellent power performance can be obtained at all vehicle speeds from low to high speeds while keeping the transmission 10 relatively compact.

In addition, in this embodiment, the gear ratio of the fifth gear is 0°848.
This setting improves fuel efficiency and quietness during high-speed driving, and provides sufficient power performance during acceleration.

In addition, each planetary gear device 16°18.2 in this embodiment
The relative rotational speed of each of the planetary gears 16p, 18p, 20p with respect to the carriers 16c, 18c, 20c is relatively low, which is advantageous in terms of the durability of the bearings and the like.

Next, another embodiment of the present invention will be described.

The transmission shown in FIG. 2 has a second
2 to the clutch, and input shaft 14, first sun gear 16s, first carrier 16c and second ring gear 18.
r and the first ring gear 1.
6r, the input shaft 14, and the first sun gear 16S are selectively connected, and as in the case of the transmission IO, the operating state is indicated by the circle in FIG. 1(b). Clutch Kl as shown in 2. 3. and brake Bl, B2. By respectively operating B3, a desired speed change gear from five forward speeds and one reverse speed is established.

The transmission shown in FIG. 3(a) is different from the transmission 10 in that a fourth clutch for selectively connecting the first sun gear 16s to the input shaft 14 is provided with 4. C)
Clutch K
l, to 2. 3. 4. and brake B1. B2. B
3 are activated, a desired speed change gear from five forward speeds and one reverse speed is established.

Note that the third clutch 3 is provided to selectively connect the input shaft 14 and the third sun gear 20S.

The transmission shown in FIG. 4(a) differs from the transmission shown in FIG. 2 in that the first clutch is changed from 1 to the first sun gear 16.
s and the second sun gear 18s are integrally connected to each other, while the first sun gear 16s and the second sun gear 18
4 is provided in the fourth clutch that selectively connects the third ring gear 2Or to the input shaft 14 whose connection with the first sun gear 16s is cut off. Furthermore, the first brake B1 is abolished to cut off the connection between the first carrier 16c and the second ring gear 18r and the transmission case 12, and the connection between the second carrier 18c and the third carrier 20c and the output gear 22 is disconnected. The connection between the first carrier 16c and the second ring gear 18 is cut off.
r and the output gear 22 are integrally connected to each other. In such a transmission, as shown in the operating state by the O mark in FIG. 4(b), the clutch Kl is
, to 3. 4. and brake B2. By respectively operating B3, a desired speed change gear from five forward speeds and one reverse speed is established. Note that in the third gear, the second clutch 2 and the third clutch 3 indicated by (○) mean that either one of the two clutches is operated. Also,
In 4th gear, 2 on the second clutch and 3 on the third clutch, indicated by (0). and 4 for the fourth clutch means that at least two of the three clutches are actuated. In addition, 1 is attached to the first clutch, and the first sun gear 16s, the second sun gear 18s, and the third
This is an engagement device that enables connection with the ring gear 2Or.

On the other hand, clutch Kl in each of the above embodiments is 2 and 3.
．． 4. and brake Bl, B2. B3 can be configured by a combination of a multi-disc clutch, a band brake, a one-way clutch, etc., and typical examples thereof are illustrated in FIGS. 5 to 15.

FIG. 5 shows a clutch consisting of a multi-disc clutch 44 and a one-way clutch 46 provided in series, and a multi-disc clutch 48 provided in parallel to them.

In FIG. 6, a one-way clutch 50 whose engagement direction is opposite to that of the one-way clutch 46 is provided in place of the one-way clutch 46 in FIG. Figure 7 shows
A multi-disc clutch 44 and a one-way clutch 46 provided in series, and a multi-disc clutch 48 and one-way clutch 50 provided in series are connected in parallel to each other. FIG. 8 shows multi-disc clutches 44 arranged in series with each other.
and a one-way clutch 46. FIG. 9 shows a clutch consisting of a multi-disc clutch 44 and a one-way clutch 50 that are arranged in parallel with each other. FIG. 10 shows a multi-disc clutch 44 and a one-way clutch 46 provided in series.
and a one-way clutch 50 provided in parallel therewith.

FIG. 11 shows multi-disc clutches 44 provided in parallel with each other.
and a one-way clutch 46. FIG. 12 shows a clutch consisting of a multi-disc clutch 44 and a one-way clutch 50 provided in series, and a one-way clutch 46 provided in parallel to them. FIG. 13 shows a one-way clutch 46 and a one-way clutch 50 provided in parallel with each other.
It consists of. FIG. 14 shows a band brake in which a band 54, one end of which is fixed to the transmission case 12, is wound around a drum 52 fixed to a member whose rotation is to be braked.

FIG. 15 shows a drum 5 fixed to a member to be rotationally braked.
6, one end of each is connected to the transmission case 12.
A pair of bands 58a fixed to.

This is a band brake in which the 58b are wound in opposite directions.

and 2. to the clutch Kl. 3. 4, brake Bl, B2. By adopting such a locking device as B3, for example, engine braking is eliminated when driving off the board or coasting, improving fuel efficiency and quietness of the vehicle, and it is also possible to apply engine braking when necessary. It becomes possible to Furthermore, when changing gears, the engagement of the one-way clutch is automatically released, thereby eliminating delicate control of the shift timing.

Although several embodiments of the present invention have been described above in detail based on the drawings, these are merely examples, and the present invention can be implemented in other embodiments.

For example, 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, in each of the above embodiments, the first planetary gear device 16, the second planetary gear device 18. Although the third planetary gear device 20 and the third planetary gear device 20 are arranged in sequence on the same axis, it is also possible to change the arrangement order of these planetary gear devices.

Further, in the embodiment described above, the output gear 22 is located on the opposite side of the engine 26 and the torque converter 24, but by disposing the input shaft 14 passing through the axis of each planetary gear device, the output gear It is also possible to arrange 22 on the side of the engine 26 and the human power converter 24.

Further, in the above embodiment, a case has been described in which five forward speeds and one reverse speed are established, but it is also possible to establish six or more forward speeds and two reverse speeds.

Further, the gear ratio of each planetary gear device and the speed ratio of each speed change gear in each of the embodiments described above may be set as appropriate.

Furthermore, it goes without saying that the locations of the brakes and clutches can be changed as necessary.

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 described in detail above, according to the planetary gear type transmission device for a vehicle of the present invention, input switching is not necessarily required when switching between adjacent transmission gears, making shift control simple and easy. becomes possible.

[Brief explanation of the drawing]

FIG. 1(a) is a schematic diagram of a planetary gear type transmission for a vehicle, which is an embodiment of the present invention. Figure 1 (0)) is Figure 1 (a)
) is a chart showing the transmission gears of the embodiment of FIG. 2 and the latches and brakes necessary to establish the gears. Figures 2 and 3 (a). FIG. 4(a) is a schematic diagram of another embodiment of the present invention. Figure 3 (b) and Figure 4 (b) are the third
FIG. 4(a) is a diagram showing the gears of the embodiment of FIG. 4E(a) and the latches and brakes necessary to establish the gears. 5 to 15 are diagrams each showing an example of a clutch and a brake that can be suitably employed in the vehicular planetary gear type transmission of the present invention. lO: Planetary gear type transmission for vehicle 14: Input shaft (input member) 16: First planetary gear unit 18: Second planetary gear unit 20: Third planetary gear unit 22: Output gear (output member) 16s: First Sun gear 16p: First planetary gear 16c:
1st carrier 16r: 1st ring gear 18s/2nd sun gear 18p: 2nd planetary gear 18c: 2nd carrier 18r: 2nd ring gear 20s: 3rd sun gear 20
p: Third planetary gear 20c: Third carrier 20r: Third
Ring gear KI: First clutch (engaging device) Applicant: Toyota Motor Corporation 16C: filffi°+7? Figure 2 Figure 3 (a) Figure 3 (b) Figure 5 Figure 6 Figure 7 Figure 8 Figure 9 Figure 10 Figure 11 Figure 12 Figure 13 Figure 14 Figure 15

Claims (1)

[Scope of Claims] A first sun gear, a first planetary gear that meshes with the first sun gear, a first ring gear that meshes with the first planetary gear, and a first carrier that rotatably supports the first planetary gear. a single pinion type first planetary gear device, a second sun gear, a second planetary gear that meshes with the second sun gear, a second ring gear that meshes with the second planetary gear, and the second sun gear.
A single pinion type second planetary gear device including a second carrier rotatably supporting a planetary gear, a third sun gear, a third planetary gear that meshes with the third sun gear, and a third ring gear that meshes with the third planetary gear. , and a single pinion type third planetary gear device including a third carrier rotatably supporting the third planetary gear are provided on the same axis, and the rotation of the input member is changed in stages to provide an output member. In a planetary gear transmission for a vehicle of a type that transmits transmission to and the third carrier can be connected at all times or by an engagement device, respectively.