JPH0318306Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a speed change steering device for an axle-equipped vehicle.

Conventionally, as shown in FIG.
Connected to pumps c ₁ and c ₂ , and the first and second pumps
A plurality of planetary gear mechanisms e, n, p with first and second motors _{d 1} and d ₂ driven by c 1 and c ₂ provided on the first shaft a.
The first shaft a is connected to the planetary gear mechanism e or the second shaft l by turning on and off a plurality of clutches k, and the planetary gear mechanism e is connected to the planetary gear mechanism e through the gear mechanism q. The second shaft l is connected to a planetary gear mechanism n via a gear mechanism g, the first output shaft h is connected to a planetary gear mechanism n, and the second shaft l is connected to a planetary gear mechanism n. A second output shaft j is connected to the planetary gear mechanism p via the gear mechanism i, and a second output shaft j is connected to the planetary gear mechanism p.
Turn on and off multiple clutches, and also turn on and off the first and second clutches.
A speed change/steering device is known that changes speed or steers left and right by changing the discharge volumes of pumps c ₁ and c ₂ . (For example, patent application No. 53-161092
No.) This device allows for smooth gear changes and steering, but on the other hand, it is possible to smoothly shift gears and steer the gear, but on the other hand, the first shaft a, the second and third shafts l and m, and the first and second pumps
Since the motors c ₁ , d ₁ , c ₂ , and d ₂ are arranged in parallel, there is a problem in that the overall size becomes very large.

The present invention was devised in view of the above circumstances, and its purpose is to provide a speed change steering system for a tracked vehicle that allows for smooth speed changes and steering, and that can be made compact as a whole.

Embodiments of the present invention will be described below with reference to FIG. 2 and subsequent figures.

An input shaft 1 connected to an engine M, which is a power source, is attached to a shaft 41. A first gear 2 and a second gear 4 are attached to the shaft 41, and the input gear 1 meshes with a third gear 10. , the third gear 10 is further meshed with the fourth gear 11.

The third gear 10 is attached to a shaft 47 so as to be relatively rotatable, and the fifth to eighth gears 13 and 1 are attached to the shaft 47.
5, 16, and 18 are installed, and the fourth
The gear 11 is attached to a cylindrical shaft 42, and the sun gear 31a and discs 53, 54 of the first planetary gear device 31 are attached to the shaft 42.

The sixth gear 15 meshes with the ninth gear 14, and a third clutch C is attached to the ninth gear 14 so as to connect the ninth gear 14 and the disc 53.

The sun gear 31a meshes with the planetary gear 31c, and the planetary gear 31c meshes with the ring gear 31.
The ring gear 31b is attached to a disc 52, and the disc 52 is engaged with the second clutch B.
It is now possible to fix it. Further, the planetary gear 31c is automatically attached to a carrier 31d, the carrier 31d is attached to a carrier 32d of the second planetary gear set 32 via a drum 43, and the fourth clutch D is connected to a disc 54 and a drum 43.
A planetary gear 32c is attached to the carrier 32d so as to be able to rotate on its own axis, and the planetary gear 32c meshes with a sun gear 32a and a ring gear 32b. 45, the tenth gear 7 and the sun gear 34a of the fourth planetary gear set 34 are attached.

The ring gear 32b is attached to the carrier 33 of the third planetary gear device 33 via a drum 44, and a planetary gear 33c is attached to the carrier 33d so as to be rotatable on its axis.
b, a disc 51 and the eleventh gear 12 are attached to the ring gear 33b, and the disc 51 can be fixed by the first clutch A, and the sun gear 33a is attached to the shaft 46, and the sun gear 33a is attached to the shaft 46. is the first
12 gear 9 and sun gear 3 of the fifth planetary gear device 35
5a is attached. The eleventh gear 12 is a fifth gear 13, the seventh gear 16 is a thirteenth gear 17,
The eighth gear 18 meshes with the fourteenth gear 19, and the thirteenth gear 1 is attached to the ring gear 34b.

The ring gear 34b meshes with the planetary gear 34c, and the planetary gear 34c meshes with the sun gear 34a.
The planetary gear 34c is rotatably attached to a carrier 34d, and the carrier 34d is attached to the first output shaft 61.

The fourteenth gear 19 is attached to a ring gear 35b, and the ring gear 35b is connected to a planetary gear 35c.
The planetary gear 35c meshes with the sun gear 35a, the planetary gear 35c is rotatably attached to a carrier 35d, and the carrier 35d is attached to the second output shaft 62.

The first gear 2 meshes with a fifteenth gear 3, and the fifteenth gear 3 is attached to the input shaft of the first continuously variable transmission 71.

The second gear 4 meshes with a 16th gear 5, and the 16th gear 5 is attached to the input shaft of the second continuously variable transmission 72.

A 17th gear 6 is attached to the output shaft of the first continuously variable transmission 71, and the 17th gear 6 meshes with the 10th gear 7, and an 18th gear 6 is attached to the output shaft of the second continuously variable transmission 72. A gear 8 is attached, and the 18th gear 8 meshes with the 12th gear 9.

Here, the first and second continuously variable transmissions 71 and 72 have an input/output rotational speed ratio (rotational speed of the 17th gear 6 or 18th gear 8 ÷ rotational speed of the 15th gear 3 or 16th gear 5)
can be changed steplessly from a negative value to a positive value. For example, there are pumps that combine a variable swash plate type axial piston pump (hereinafter referred to as a hydraulic pump) and a fixed (or variable) swash plate type axial piston motor (hereinafter referred to as a hydraulic motor), or combinations of a generator and an electric motor. .

Next, the operation will be explained.

(1) In the case of the first speed gear The first clutch A is engaged, and the second, third, and fourth clutches B, C, and D are disengaged.

The power input to input gear 1 is transmitted to the 1st, 15th, 2nd,
16th gear 2, 3, 4, 5, 1st and 2nd continuously variable transmission 71, 72, 17th, 10th, 8th and 12th gear 6,
4th and 5th planetary gear set 3 via 7, 8, 9
The signal is transmitted to sun gears 34a and 35a of numbers 4 and 35.

On the other hand, the 11th and 5th gears 1 are
This is because the shaft 47 is fixed via 2 and 13.
Ring gears 34b and 35b are fixed by clutch A.

Therefore, power is transmitted from the carriers 34d and 35d to the first and second output shafts 61 and 62.

In this state, the first and second continuously variable transmissions 71 and 72
By increasing the input/output rotational speed ratio from 0, the rotational speed of the first and second output shafts 61 and 62 also becomes 0.
By reversing the output rotation of the continuously variable transmissions 71 and 72, the first
The second output shafts 61 and 62 are also reversed.

By appropriately selecting the number of teeth of each gear, the second clutch is activated when the input/output rotational speed ratio of the first and second continuously variable transmissions 71 and 72 reaches a certain value (>0) at the first speed stage. The relative rotational speed of B can be set to 0 (the state in which the disk 52 is stationary). At this time, if the second clutch B is engaged and the first clutch A is disengaged, the gear can be shifted to the second speed without any shock. At this time, there is no change in the rotational speed of each part.

(2) Second speed stage The second clutch B is engaged, and the first, third, and fourth clutches A, C, and D are disengaged.

The input/output rotational speed ratio of the first and second continuously variable transmissions 71 and 72 is switched to the second speed at a certain value, and the input/output rotational speed ratio of the first and second continuously variable transmissions 71 and 72 is then decreased. The rotational speeds of the first and second output shafts 61 and 62 increase. In other words, part of the power that enters input gear 1 is transferred to the 1st, 15th, 2nd, and
16 gears 2, 3, 4, 5, 1st and 2nd continuously variable transmission 7
1, 72, 17th, 10th, 18th, 12th gear 6, 7,
8, 9 to the second to fifth planetary gear devices 32, 3
3, 34, 35 sun gears 32a, 33a, 34
a, 35a.

On the other hand, since the clutch B is engaged, the first planetary gear set 31 is in an operating state (power transmitting state), and a part of the power that has entered the input gear 1 is transferred to the third and fourth planetary gears.
It is transmitted to the carrier 32d via the gears 10, 11, the gear 31a, the planetary gear 31c, the carrier 31d, and the drum 43. Here the sun gear 32a
The power transmitted to the ring gear 32 is combined with the power transmitted to the ring gear 32.
b, transmitted to the carrier 33d via the drum 44; Here again, the power is combined with the power transmitted to the sun gear 33a and transmitted to the shaft 47 via the ring gear 33b and the 11th and 5th gears 12, 13.
Here, the power of 7th, 13th, 8th, 14th gear 1
The signal is transmitted via gears 6, 17, 18, and 19 to the ring gear 34b and ring gear 35b of the fourth and fifth planetary gear units 34 and 35, respectively.

Then, the power is combined from the ring gear 34b and the sun gear 34a, and is transmitted to the first gear via the carrier 34d.
The power is transmitted to the output shaft 61, and the power is combined from the ring gear 35b and sun gear 35a to the carrier 35d.
is transmitted to the second output shaft 62 via.

When the input/output rotational speed ratio of the first and second continuously variable transmissions 71 and 72 is decreased, the shaft 47 speeds up via the second and third planetary gear devices 32 and 33, and the ring gears 34b and 34b speed up. Along with Sun Gear 34
a, 35a decelerate. However, by appropriately selecting the number of gear teeth, the rotational speed of the first and second output shafts 61 and 62, which are a combination of the ring gears 34 and 35b and the sun gears 34a and 35a, increases.

The input/output rotational speed ratio of the first and second continuously variable transmissions 71 and 72 is decreased, passing through 0 and becoming a negative speed ratio, and when it reaches a certain value, the relative rotational speed of the third clutch C becomes 0. At this time, if the third clutch C is engaged and the second clutch B is disengaged, the gear can be shifted to the third speed without any shock. At this time, there is no change in the rotational speed of each part.

(3) Third speed stage The third clutch C is engaged, and the first, second, and fourth clutches A, B, and D are disengaged.

The input/output rotational speed ratio of the first and second continuously variable transmissions 71 and 72 is switched to the third speed at a certain value, and this time the input/output rotational speed ratio of the first and second continuously variable transmissions 71 and 72 is changed. As it increases, the first and second output shafts 61
The rotational speed of and 62 increases.

In other words, part of the power input to the input gear 1 is transferred to the first, 15th, second, and 16th gears 2, 3, 4, and 5, the first and second continuously variable transmissions 71, 72, and the 17th and 16th gears. 10th
18. Sun gears 34a, 35a of the 4th and 5th planetary gear units 34, 35 via the 12th gears 6, 7, 8, 9
to communicate.

On the other hand, since the third clutch C is engaged, part of the power input to the input gear 1 is transferred to the third and fourth gears 10,
11, the shaft 42, the disc 53, the clutch C, the ninth and sixth gears 14, 15, and the shaft 47.
The power of 7 is the 7th, 13th, 8th, and 14th gear 16, 1
The ring gear 34b and the ring gear 35 of the fourth and fifth planetary gear units 34 and 35 are
It is divided into two parts and transmitted. and ring gear 34
Power is combined from the ring gear 35b and the sun gear 35b and transmitted to the first output shaft 61 via the carrier 34d, and power is combined from the ring gear 35b and the sun gear 35a and transmitted to the second output shaft 62 via the carrier 35d.
to communicate.

When the input/output rotational speed ratio of the first and second continuously variable transmissions 71 and 72 increases and passes through 0 to a positive speed ratio and reaches a certain value, the relative rotational speed of the fourth clutch D becomes 0. At this time, if the fourth clutch D is engaged and the third clutch C is disengaged, the gear can be shifted to the fourth speed without any shock. At this time, there is no change in the rotational speed of each part.

(4) Fourth speed stage The fourth clutch D is engaged, and the first to third clutches A, B, and C are disengaged.

The input/output rotational speed ratio of the first and second continuously variable transmissions 71 and 72 is switched to the fourth speed at a certain value, and this time the input/output rotational speed ratio of the first and second continuously variable transmissions 71 and 72 is changed. As it decreases, the first and second output shafts 61
The rotational speed of and 62 increases.

Here, the difference between the second speed and the fourth speed is only the reduction ratio from the input gear 1 to the carrier 32d; in the second speed, the reduction ratio is large due to the first planetary gear device 31,
In the fourth speed, the reduction ratio is reduced by the fourth clutch D. Other operations are the same as in the second speed, so explanations will be omitted.

(5) Steering By making a difference in the input/output rotational speed ratio of the first and second continuously variable transmissions 71 and 72, a difference is created in the rotational speed of the first and second output shafts 61 and 62, causing the vehicle to turn. be able to.

That is, in any state of the first speed, second speed, third speed, and fourth speed, the fourth and fifth planetary gear devices 3
4 and 35 ring gears 34b and 35b are connected to the shaft 47
are at the same rotation speed through. Therefore, the difference in rotational speed between the first and second output shafts 61 and 62 during running is determined by the difference in rotational speed between the sun gears 34a and 35a. Therefore, by making a difference between the input and output rotational speed ratios of the first and second continuously variable transmissions 71 and 72, it is possible to steplessly change the rotational speed difference between the output shafts 61 and 62, that is, the turning radius of the vehicle.

As mentioned above, you can shift gears smoothly,
Can be steered.

Further, since each of the planetary gear units 31 to 35 and each of the clutches A to D are arranged coaxially, the entire system can be made compact.

In addition, in FIG. 2, the first and second continuously variable transmissions 71 and 72 are each of an integral type, but
When using a combination of a hydraulic pump and a hydraulic motor or a generator and an electric motor, if the combination of a hydraulic pump and a hydraulic motor or a generator and an electric motor is used in an integrated format, the axial length will be long and the overall structure cannot be made compact. By separately placing the motor or generator and the electric motor, the overall size can be made more compact.

That is, the gear 20 is attached to the shaft 41, and the gear 20 is attached to the shaft 41.
At the same time, the gear 21 is attached to the input shaft of the hydraulic pump (or generator) 71a and 72a, and the piping (or electric Power is transmitted through a hydraulic pump (or generator) 72a to a hydraulic motor (or electric motor) 72b through piping (or electrical wiring) 82.

The present invention is as described above, and the first, second, third,
By engaging and disengaging the fourth clutches A, B, C, and D, the rotational speeds of the first and second output shafts 61 and 62 can be changed to change the speed, and the first and second output shafts can be continuously variable. The first output shaft 61 and the second output shaft 62 are made different by making a difference in the input/output rotational speed ratio of the machines 71 and 72.
A difference occurs in the rotational speed of the two wheels, allowing the vehicle to be steered left and right.

Therefore, it is possible to shift gears and steer smoothly.

In addition, the first, second, third, fourth, and fifth planetary gear devices 31, 32, 33, 34, and 35 are arranged on the same axis,
Moreover, since they are arranged at intervals in the axial direction, the whole can be made compact.

Also, the ring gear 32 of the second planetary gear mechanism 32
b and the carrier 33d of the third planetary gear mechanism 33, the rotation direction of both sun gears 32a, 33a can be made the same, and since the shaft 46 can be integrally connected directly to the second continuously variable transmission 72, the rotation can be controlled. The structure can be simplified without requiring gears for reverse.

[Brief explanation of drawings]

FIG. 1 is an explanatory diagram of a conventional example, and FIGS. 2 and 3 are explanatory diagrams showing different embodiments of the present invention. 31, 32, 33, 34, 35 are first to fifth planetary gear units, 71, 72 are first and second continuously variable transmissions, and A, B, C, and D are clutches.

Claims (1)

[Scope of utility model registration request] A cylindrical shaft 42 connected to a power source, a first planetary gear unit 31, a second planetary gear unit 32, a third planetary gear unit 33, a fourth planetary gear unit 34, and a fifth planetary gear unit 35 are coaxially connected to each other. A shaft 47, a first continuously variable transmission 71, and a second continuously variable transmission capable of steplessly changing the input/output rotational speed ratio are disposed at intervals in the direction and adjacent to each of these planetary gear devices. 72 are arranged in parallel, and the sun gear 31 of the first planetary gear device 31
a to the shaft 42, a second clutch B which connects the carrier 31d to the carrier 32d of the second planetary gear set 32 by a drum 43, and fixes the ring gear 31b, and a fourth clutch B which connects the drum 43 and the shaft 42. A clutch D is provided, which connects the sun gear 32a of the second planetary gear set 32 to the shaft 45 inserted into the shaft 42, and connects the ring gear 32b to the carrier 33d of the third planetary gear set 33. A first clutch A is provided which is connected to the shaft 47 via a gear and which fixes the ring gear 33b.
4a is the shaft 45, and the carrier 34d is the first output shaft 6.
1. The ring gear 34b is connected to the shaft 47 via a gear.
The sun gear 35a of the fifth planetary gear set 35 is connected to the shaft 46, and the carrier 35d is connected to the second
The output shaft 62 and the ring gear 35b are connected to the shaft 47 via gears, and a third clutch c is provided to connect the shaft 42 and the shaft 47, and the output of the first and second continuously variable transmissions 71 and 72 is A speed change steering device for a tracked vehicle, characterized in that the sides are connected to the shafts 45 and 46, and the input side is connected to a power source.