JPH0769008B2 - Gearbox - Google Patents

Description

Description: [Industrial field of application] The present invention relates to a transmission applied to a vehicle transmission or the like.

[Prior Art] A transmission for a vehicle is, for example, a gearshift in which one of a plurality of pairs of gears that are constantly meshed is coaxially arranged and a shaft and gears are selectively coupled by a sleeve that slides on a shaft spline. Machine has been adopted.

[Problems to be Solved by the Invention] In the case of the above-mentioned transmission, there is a problem that a mechanism is complicated because a synchronizing device for synchronizing the rotation of a gear to be coupled with the rotation of a shaft is required.

The present invention aims to solve the above problems.

[Means for Solving the Problem] The transmission of the present invention includes an input gear, an output gear, and a planetary gear between an input shaft and an output shaft that are concentrically arranged apart from each other in the axial direction. The first differential gear train, the second differential gear train, and the third differential gear train are fixed to the input shaft with the first input gear of the first differential gear train, and the third differential gear train is used as the output shaft. The first output gear of the first differential gear train is fixed between the input shaft and the output shaft while being arranged in series so as to be capable of transmitting rotation, and the rotational operation of the first output gear is controlled by the second output gear. The first transmission shaft that transmits to the differential gear train and the first planetary gear arm that supports the first planetary gear of the first differential gear train are fixed, and the first planetary gear rotates by the revolution number of the first planetary gear and the first planetary gear. Third revolution of gears
A second transmission shaft for transmitting to the differential gear train and a third transmission shaft for fixing the second output gear of the second differential gear train and transmitting the rotational operation of the second output gear to the third differential gear train. Are installed concentrically so as to be movable together in the axial direction, and are movable on the first transmission shaft so as to be screwed to the input shaft side and the output shaft side and linked to the second differential gear train. The shaft is fitted so as to be movable together in the axial direction, and an input shaft, a first transmission shaft, and a second transmission shaft are provided near the first differential gear train when the movable shaft is screwed to the input shaft side. Is provided with a first clutch for connecting the shafts such that the shafts rotate integrally, and a first brake for contacting with and separating from the first planetary gear arm to stop and release the second transmission shaft. A second brake that stops and releases the third transmission shaft by contacting and separating from the second output gear is provided near the train, and a front brake is provided near the third differential gear train. A second clutch is provided to connect the second transmission shaft, the third transmission shaft and the output shaft so that the shafts rotate integrally when the movable shaft is screwed to the output shaft side. Installed so that it can be tilted, 90 from the input shaft direction
A first gear shift position that has changed direction, a second gear shift position in the direction of the output shaft, and a third gear position that has changed 180 degrees from the first gear shift position.
An operation lever tilted from a neutral position to a gear shift position and a fourth gear shift position in the input shaft direction is engaged with a gear portion formed on the movable shaft, and the operation lever is moved to the first gear shift position and the first gear shift position. A sector gear is formed to screw the movable shaft to the output shaft side and the input shaft side when tilted to the third shift position, and the operation lever and the first brake are tilted to the fourth shift position. At times, the first brake is linked by the operation lever so that the first brake is pressed against the first planetary gear arm, and the operation lever and the second planetary gear arm are connected together.
The brake and the brake are linked so that when the operation lever is tilted to the second shift position, the second brake is pressed by the operation lever and pressed against the second output gear.

(Operation) In the transmission having the above-described configuration, when the operation lever is tilted to the first shift position, the movable shaft is screwed toward the output shaft side and the second clutch is engaged, so that the first and second differential gear trains are engaged. Differentially rotates, and the second transmission shaft, the third transmission shaft, and the output shaft rotate integrally. When the operation lever is tilted to the second gear position, the second brake is pressed by the operation lever and pressed against the second output gear, and the second output gear and the third transmission shaft are stopped by the second brake and the third transmission shaft is stopped. The output rotation of the third differential gear train is transmitted to the output shaft in a state where the rotation is not transmitted to the third differential gear train. When the operation lever is tilted to the third speed change position, the movable shaft is screwed toward the input shaft side and the first clutch is engaged, and the input shaft, the first transmission shaft and the second transmission shaft are integrally rotated to move to the first position. 2, the third differential gear train differentially rotates, and the output rotation of the third differential gear train is transmitted to the output shaft. Operation lever is 4th
When tilted to the shift position, the first brake is pushed by the operation lever and pressed against the first planetary gear arm, the first planetary gear arm and the second transmission shaft are stopped, and the rotation of the second transmission shaft rotates by the third difference. The output rotation of the third differential gear train is transmitted to the output shaft without being transmitted to the dynamic gear train, and the rotational speed of the output shaft is switched to four stages by tilting the operating lever in four directions.

EFFECTS OF THE INVENTION Since the present invention is configured as described above, the output rotation speed can be accurately shifted in four steps by tilting the operating lever in four directions, and the gear meshing position can be changed. Since gear shifting is not performed, gear shifting operation can be smoothed to reduce gear wear and component failure, and since there is no need for a synchronizing device or the like, the entire gear shifting mechanism can be made compact.

[Embodiment] Next, an embodiment of the present invention will be described with reference to FIGS.

An input shaft 2 and an output shaft 3, which are coaxially arranged, are rotatably supported by bearings 4 and 4 at both ends of a gear case 1 of the transmission H, and between the input shaft 2 and the output shaft 3. The second transmission shaft 5 is laterally mounted coaxially with the input shaft 2 and the output shaft 3 so as to be rotatable and axially movable.

In the gear case 1, a first differential gear train G1 arranged on the input shaft 2 side, a second differential gear train G2 arranged near an intermediate portion between the input shaft 2 and the output shaft 3, and an output Third installed on the shaft 3 side
The differential gear train G3 is arranged in series.

In the first differential gear train G1, the first input gear 6 is fixed to the input shaft 2 and the first planetary gear arm 7 fixed to the second transmission shaft 5 and having the braking receiving portion 7a is formed. A first planetary gear 8 that is inscribed in mesh with the first input gear 6 is rotatably supported, and is further mounted on the second transmission shaft 5 so as to be rotatable and axially movable. A first output gear 10 circumscribing and meshing with the first planetary gear 8 is provided at the end of the input shaft 2 on the side of the input shaft 2.
Is fixed.

Between the first input gear 6 and the first planetary gear arm 7, and the first
The first clutch 11, which is engaged and disengaged with the axial movement of the first transmission shaft 9, is provided between the flange portion 9a projectingly formed on the transmission shaft 9 and the braking receiving portion 7a of the first planetary gear arm 7. When the first transmission shaft 9 moves toward the input shaft 2 side, the first clutch 11 and the first clutch 11 are engaged to connect the first input gear 6, the first planetary gear arm 7, and the first transmission shaft 9, respectively. Rotate integrally.

In the second differential gear train G2, the second input gear 12 is fixed to the end of the first transmission shaft 9 on the output shaft 3 side, and is fitted to the first transmission shaft 9 so as to be rotatable and movable in the axial direction. A second planetary gear arm 15 is fixed to the mounted movable shaft 13, and a second planetary gear 14 circumscribing and meshing with the second input gear 12 is rotatably supported on the second planetary gear arm 15. Further, the second planetary gear 14 is attached to the input shaft 2 side end portion of the third transmission shaft 16 which is fitted so as to be rotatable and axially movable near the output shaft 3 side end portion of the second transmission shaft 5. The second output gear 17, which is circumscribed and meshed, is fixed.

The bearings 39, 3 are arranged so that the movable shaft 13 moves together with the first transmission shaft 9 toward the input shaft 2 and moves together with the third transmission shaft 16 toward the output shaft 3 side.
It is pinched between the nine.

The movable shaft 13 is formed with a left-hand screw portion 19 screwed into a screw hole 18a of a partition wall 18 vertically provided in the gear case 1 and a gear portion 20 adjacent to each other.

In the third differential gear train G3, the third input gear 22 is fixed to the third transmission shaft 16 and the output shaft 3 of the second transmission shaft 5 is provided.
A third output gear 23 is fixed to the side end portion, and a third planetary gear arm 24 fixed to the output shaft 3 has a third input gear 22 and a third output gear 23.
A pair of inner and outer third planetary gears 25 meshed with each other to rotate the output gear 23 in the same direction is rotatably supported,
The inner third planetary gear 25 is circumscribed and meshed with the third input gear 22, while the outer third planetary gear 25 is internally meshed with the third output gear 23.

Flange formed on the end of the third transmission shaft 16 on the output shaft 3 side
The second clutch 27, which is disengaged between the third input gear 22 and the third input gear 22 and between the third input gear 22 and the third planetary gear arm 24 by the movement of the third transmission shaft 16 in the axial direction, When the third transmission shaft 16 is moved toward the output shaft 3 side, both second clutches 27 are engaged and the third transmission shaft 16 is engaged.
16, the third output gear 23, and the output shaft 3 rotate integrally.

Operation of tilting in four directions in order to unilaterally stop and release the second transmission shaft 5 and the third transmission shaft 16 and to unilaterally connect and disconnect the first clutch 11 and the second clutch 27. The lever 28 is attached to the central portion of the upper surface of the gear case 1 by a pin 29 parallel to the axis of the second transmission shaft 5 so as to be tiltable in the left-right direction, and is suspended in the gear case 1. The operating portion 28a is connected to the upper end of the operating portion 28a by a pin 30 orthogonal to the shaft 5 so as to be tiltable in the front-rear direction and protrudes above the gear case 1. The operating portion 28b is provided at the center of the upper surface of the gear case 1. The first shift position P, which is inserted into the + shaped positioning hole 31a penetrating the attached control box 31, and which turns the operation lever 28 by 90 ° counterclockwise from the input shaft direction.
And 90 ° counterclockwise from the first shift position P in the output shaft direction.
180 degrees from the second gear shift position N and the first gear shift position
The tilting operation can be selectively performed from the neutral position in the four directions of the third gearshift position T that is changed in direction and the fourth gearshift position M that is changed in direction by 180 ° from the second gear position in the input shaft direction.

At the lower end of the operating portion 28a of the operating lever 28, the gear portion 2 of the movable shaft 13 is provided.
While the sector gear 32 meshing with 0 is formed, the operating portion 28b of the operating lever 28 swings back and forth in the gear case 1 to brake and release the second transmission shaft 5 via the first planetary gear arm 7. The first brake 33 movably supported is the link 34.
It is linked so that it can be linked via.

The second brake 36 opposed to the second output gear 17 for braking and releasing the third transmission shaft 16 via the second output gear 17 is urged upward by the spring 35, and the second brake 36 Brake shoe 37 curved in an arc shape on the lower end surface
On the other hand, an interlocking piece 36a is formed at the upper end of the second brake 36 so as to be opposed to the projecting piece 28c of the operating lever 28.

When the operating lever 28 is tilted to the first gear shift position P, the movable shaft 13 rotates counterclockwise, the screw portion 19 is screwed toward the output shaft 3 side, and both the second clutches 27 are engaged, and the third clutch 27 is engaged. Differential gear train
G3 and the third transmission shaft 16 rotate integrally. Operating lever 28
When tilted to the third shift position T, the movable shaft 13 rotates in the clockwise direction, the screw portion 19 is screwed toward the input shaft 2 side, and both first clutches 11 are engaged, and the first differential gear train is engaged. G1 and the first transmission shaft 9 rotate integrally.

When the operating lever 28 is tilted to the second speed change position N,
The brake 36 is pushed down by the projecting piece 28a of the operating lever 28, the brake shoe 37 is pressed against the second output gear 17, and the second output gear, the third input gear 22 and the third transmission shaft 16 are stopped.

When the operating lever 28 is tilted to the fourth shift position M, the first
When the brake is pressed against the brake receiving portion 7a of the first planetary gear arm 7 to stop the first planetary gear arm 7 and the second transmission shaft 5, and when the operating lever 28 is held in the neutral position, the first and second The clutches 11 and 27 are separated, the first and second brakes 33 and 36 are separated from the first planetary gear arm 7 and the second output gear 17, respectively, and the input shaft 2, the first transmission shaft 9 and the second transmission The shaft 5 and the third transmission shaft 16 each idle.

Here, the gear ratio Z6 / Z10 = a1 between the first input gear 6 and the first output gear 10 of the first differential gear train G1 is set, and the second input gear 12 and the second input gear 12 of the second differential gear train G2 are Tooth ratio with output gear 17 Z17 / Z12 = a
2, and the tooth number ratio of the third input gear 22 and the third output gear 23 of the third differential gear train G3 is Z23 / Z22 = a3.

If Rn is the number of rotations of each member, R2 = R6, R7 = R5 =
R23, R10 = R12, R15 = 0, R17 = R16 = R22, R24 = R3.

Then, when the operating lever 28 is tilted to the first gearshift position P, the second clutch 27 is engaged and the third differential gear train G3 and the third transmission shaft 16 are integrally formed at the rotation speed R7 of the first planetary gear arm 7. Rotating to R7 = R22 = R23 = R24 = R3, so -a1 = (R10-R3) / (R2-R3), R12 = R10 = -a2, a3, and the first gear ratio H1, that is, the input The ratio of the output rotation speed R3 to the rotation speed R2 is H1 = R3 / R2 = a1 / (a1 + a2 + 1).

When the speed change lever 28 is tilted to the second speed change position N,
Since the transmission shaft 16 and the second output gear 17 are stopped by the second brake 36 and the second planetary gear arm 15 is stationary, the first transmission shaft 9 is stationary and the input rotation of the first input gear 6 causes the first rotation. The first planetary gear 8 revolves, the second transmission shaft 5 and the third output gear 23 rotate at the revolution speed of the first planetary gear 8, and the third planetary gear arm 24 and the output shaft 3 have the third input gear 22 stationary. It rotates at the revolution speed of the 3rd planetary gear 25 in the state. In this case
Since R17 = R22 = R15 = R9 = 0, 1 / a1 = R7 / (R2-R7), R7 = R2 / (a1 + 1), and the second gear ratio H2 is H2 = R3 / R2 = a1 ・ a3 It becomes / (a1 + 1) (a3 + 1).

When the operating lever 28 is tilted to the third gear shift position T, the first clutch 11 is engaged and the first differential gear train G1 and the first transmission shaft 9 rotate integrally, and R2 = R6 = R23. Therefore, -1 / a3 = (R2-R3) / (R17-R3), R17 = -R2 / a2, and the third gear ratio H3 is H3 = R3 / R2 = (a2 ・ a3-1) / a2 ( a3 + 1).

Further, when the operation lever 28 is tilted to the fourth shift position M, the first planetary gear arm 7 is stopped, the second transmission shaft 5 and the third output gear 23 are stopped, and R7 = R23 = 0. R10 = -a1 ・ R2, R17 = -R10 / a2, 1 / a3 = -R3 / (R17-R3), and the fourth gear ratio H4, that is, the ratio of the output speed R3 to the input speed R2 is H4 = R3. / R2 = a1 / a2 (a3 + 1). However, when H4 <0 <H1 <H2 <H3 and the operating lever 28 is tilted to the third shift position M, the output shaft 3 is rotated in the reverse direction.

For example, when a1 = 5/2, a2 = 3, a3 = -4, H1 = 5
/ 13, H2 = 20/21, H3 = 13/9, H4 = -5/18.

FIG. 6 (A) is a diagram showing the relationship between the rotation speed R9 of the first transmission shaft 9, the rotation speed R5 of the second transmission shaft 5, the rotation speed R16 of the third transmission shaft 16, and the output rotation speed R3. Is.

Next, a second embodiment shown in FIG. 4 will be described. In this embodiment, the first planetary gear 8 is in external contact with the first input gear 6 and inscribed in the first output gear 10, and is meshed with the first planetary gear 8 to form the first transmission. The second planetary gear arm 15 is fixed to the shaft 9, the second input gear 12 is fixed to the second transmission shaft 13, and one third planetary gear 25 is pivotally supported by the third planetary gear arm 24. The structure is substantially the same as that of the first embodiment except the above.

In the second embodiment, R2 = R6, R7 = R5 = R23, R10 = R15, R12 =
0, R17 = R16 = R22, R24 = R3.

Then, when the operation lever 28 is tilted to the first speed change position P, R22 = R23 = R24 = R3, so that the first speed ratio H1
Is Becomes

Further, when the operation lever 28 is tilted to the second shift position N, R17 = R22 = 0 and R10 = R15 = 0, so the second gear ratio H2 is H2 = a1 · a3 / (a1 + 1) (a3 + 1). Become.

Further, when the operation lever 28 is tilted to the third speed change position T, R2 = R6 = R7 = R10, so the third speed ratio H3 becomes H3 = R3 / R2 = (a2.a3 + a2 + 1) / a2 (a3 + 1). .

Further, when the operation lever 28 is tilted to the fourth speed change position M, R17 = R23 = 0, so the fourth speed ratio H4 becomes H4 = R3 / R2 = -a1 (a2 + 1) / a2 (a3 + 1).

However, H4 <0 <H2 <H1 <H3 FIG. 6 (B) shows the first to third transmission shafts 9, 5, 16 of the second embodiment.
6 is a diagram showing the relationship between the rotation speeds R9, R5, R16 of FIG.

Next, the third embodiment shown in FIG. 5 will be explained. In this embodiment, the third input gear 22 circumscribing and meshing with the third planetary gear 25 is fixed to the third transmission shaft 16, and the transmission shaft 5 The third planetary gear arm 24 is fixed to the output shaft 3, and the third output gear 23 inscribed in mesh with the third planetary gear 25 is fixed to the output shaft 3, and the movable shaft is movable.
The structure is similar to that of the second embodiment except that the threaded portion 19 of 13 is a right-handed thread.

In the third embodiment, R2 = R6, R7 = R5 = R24, R10 = R9 = R15, R
12 = 0, R17 = R16 = R22, R23 = R3.

Then, when the operation lever 28 is tilted to the first speed change position P, R22 = R23 = R24 = R3, so that the first speed ratio H1
Is Becomes

Further, when the operation lever 28 is tilted to the second gear shift position N, R17 = R22 = 0 and R15 = R9 = 0, so the second gear ratio H2 is H2 = R3 / R2 = a1 (a3 + 1) / a3 ( a1 + 1).

Further, when the operation lever 28 is tilted to the third speed change position T, R2 = R6 = R7 = R10, so the third speed ratio H3 is Becomes

Further, when the operating lever 28 is tilted to the fourth gear shift position M, R7 = R24 = 0, so the fourth gear ratio H4 becomes H4 = a1. (A2 + 1) /a2.a3.

However, 0 <H3 <H1 <H2 <H4 FIG. 6 (C) shows the rotational speeds R9, R5, R16 of the first to third transmission shafts 9, 5, 16 of the third embodiment and the output rotational speed R3. It is a diagram showing the relationship of.

Therefore, in any case, the output rotation speed can be accurately shifted in four steps by tilting the operating lever 28 in four directions, and the gear meshing position is not changed so that gear shifting is not smoothed. It is possible to reduce wear and damage to parts and reduce the size of the entire transmission mechanism because a synchronizing device and the like are not required. Further, in addition to gear shifting by tilting the operating lever 28, the screw portion 19 of the movable shaft 13 rotates clockwise or counterclockwise due to a change in the balance between the input and the output, and the first clutch 11 and the second clutch Since 27 and 27 are automatically disengaged and coupled, the operation force at the time of shifting can be reduced and the shifting operation can be simplified.

[Brief description of drawings]

1 to 3 show a first embodiment of the present invention. FIG. 1 is a longitudinal sectional view of a transmission, FIG. 2 is a view taken along the line X1-X1 of FIG. 1, and FIG. Is also the X2-X2 line arrow view, and FIG. 4 is the second
FIG. 5 is a vertical sectional view of the transmission of the embodiment, FIG. 5 is a vertical sectional view of the transmission of the third embodiment, and FIGS. 6 (A), (B), and (C) are the first to third embodiments. It is a diagram which shows the relationship between the rotation speed of a transmission shaft, and an output rotation speed, respectively. G1 ... first differential gear train G2 ... second differential gear train G3 ... third differential gear train 2 ... input shaft 3 ... output shaft 5 ... second transmission shaft 6 ... first input gear 8 ... first planetary gear 9 ... 1st transmission shaft 10 ... 1st output gear 16 ... 3rd transmission shaft 17 ... 2nd output gear

Claims (1)

[Claims] 1. A first differential gear train and a second differential gear train, each of which has an input gear, an output gear and a planetary gear between an input shaft and an output shaft which are concentrically arranged apart from each other in the axial direction. The gear train and the third differential gear train are arranged in series in a state in which the first input gear of the first differential gear train is fixed to the input shaft and the third differential gear train is rotatably linked to the output shaft. In addition, the first output gear of the first differential gear train is fixed between the input shaft and the output shaft, and the first transmission shaft for transmitting the rotational operation of the first output gear to the second differential gear train. And the first planetary gear arm supporting the first planetary gear of the first differential gear train is fixed, and the first planetary gear revolves by rotating at the revolution number of the first planetary gear to the third differential gear train. And the second output gear of the second differential gear train are fixed, and the rotational movement of this second output gear is transmitted to the third differential gear train. A third transmission shaft is installed concentrically so as to be movable in the axial direction, and the first transmission shaft is installed in the second differential gear train so as to be screwed to the input shaft side and the output shaft side. The linked movable shafts are fitted so as to be movable together in the axial direction, and in the vicinity of the first differential gear train, when the movable shafts are screwed to the input shaft side, the input shaft, the first transmission shaft, and the A first clutch that connects the two transmission shafts so that the shafts rotate integrally; and a first brake that contacts and separates from the first planetary gear arm to stop and release the second transmission shaft. A second brake for stopping and releasing the third transmission shaft by contacting and separating from the second output gear is provided near the second differential gear train, and the movable shaft is provided on the output shaft side near the third differential gear train. A second clutch is provided to connect the second transmission shaft, the third transmission shaft, and the output shaft so that the shafts rotate integrally when they are screwed in. A first gear shift position which is installed tiltably between the two brakes and which is turned by 90 ° from the input shaft direction, a second gear shift position which is turned by the output shaft direction, and a first gear shift position which is turned by 180 ° from the first gear shift position. The operation lever, which is tilted from the neutral position to the third shift position and the fourth shift position in the input shaft direction, is meshed with a gear portion formed on the movable shaft, and the operation lever is moved to the first shift position and the first shift position. Forming a sector gear for screwing the movable shaft to the output shaft side and the input shaft side when the movable shaft is tilted to the third shift position,
The operation lever and the first brake are linked so that when the operation lever is tilted to the fourth shift position, the first brake is pressed by the operation lever and pressed against the first planetary gear arm; The operation lever and the second brake are linked so that the second brake is pushed by the operation lever and pressed against the second output gear when the operation lever is tilted to the second shift position. Gearbox.