JPS601498B2 - transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a transmission for a vehicle such as an automobile, and particularly to a transmission equipped with a dramatic transmission.

As a transmission for a vehicle such as a car, there is a main transmission that is manually operated to switch between a plurality of gears, and a main transmission that is provided separately from the main transmission and that switches between a high speed and a low speed. 2. Description of the Related Art There is a known transmission device that has a sub-transmission device that can be switched, and is configured so that each of the main transmission device and the sub-transmission device can perform a shift change.

This transmission with an auxiliary transmission can obtain a large number of gears, and by effectively utilizing each gear, the engine can be operated at the rotational speed and rotational power that match various driving conditions. This allows the engine's maximum output to be used effectively under a variety of driving conditions, improving engine power performance, fuel efficiency, and quietness. Conventionally, a dramatic change gear has a direct gear and a speed increasing gear, and is provided between an output shaft (transmission main shaft) and a drive shaft (propeller shaft) of a main transmission.

In this case, in the sub-transmission, the input shaft (clutch shaft) of the main transmission is directly connected to the output shaft, and the gear ratio is 1.
Rotational power is transmitted in all gears of the main transmission including the top range. By the way, in the case of the top range in which the input gear and output shaft of the main transmission are directly connected, the sub-transmission is switched to the direct-coupled gear and only transmits rotational power and does not perform any actual gear shifting.
In this case, the rotational power of the input shaft may be transmitted directly to the drive shaft via the output shaft, bypassing the sub-transmission, and thereby the life of the sub-transmission can be extended. In addition, in normal driving, the top range is used most frequently (time), so if the rotational power is not transmitted to the sub-transmission when the top range is used as described above, then the sub-transmission The effect of extending the life of the device is significant. The present invention focuses on the above-mentioned recognition, and aims to extend the life of the sub-transmission by preventing rotational power from being transmitted to the sub-transmission when in the top range.
It is an object of the present invention to provide a transmission with an improved sub-transmission.

According to the present invention, an input shaft, an output shaft disposed on the same edge as the input shaft, a counter shaft disposed parallel to the output shaft, and a counter shaft disposed on the same axis as the counter shaft. A mechanism that transmits the rotational power given from the input gear to the counter shaft at one speed ratio selected from a speed ratio of 1 and another finite value different from this. a gear that is carried by the counter shaft and rotates in the same direction as the counter shaft; and a gear that is carried by the output shaft and rotates in the same direction as the output shaft; A plurality of gears providing gear trains with a plurality of different gear ratios between the output shaft and the gear train, and only one selected of the plurality of gear trains is in a driving force transmission state and the other gear trains are provided with driving force. This is achieved by a transmission device characterized in that it has a synchronizer that sets an idle rotation state in which no signal is transmitted, and a synchronizer that selectively directly connects the input shaft and the output shaft.

Since the sub-transmission device is provided between the input shaft and the counter shaft, in the top range where the input shaft and output shaft are directly connected by the coupling device, the rotational power of the input shaft is
The signal is transmitted directly to the output shaft, and from the output shaft to the drive shaft that is directly connected to the output shaft, so even if the sub-transmission gear rotates at this top range, it will never idle. Therefore, rotational power is not transmitted. Therefore, the period during which the auxiliary transmission transmits rotational power is shortened,
The lifespan will be longer accordingly. DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described in detail below with reference to the accompanying drawings.

The attached FIG. 1 is a skeleton diagram showing one embodiment of a transmission according to the present invention.

In FIG. 1, reference numeral 1 indicates a part of an engine, and the rotational power output from the engine 1 is transmitted to an input shaft 4 of a transmission 3 via a clutch device 2.
The transmission 3 includes, in its case 5, a synchronized mesh type main transmission 7 with four forward speeds and one reverse speed, and a two-stage planetary gear type auxiliary transmission 30. The input shaft 4 is rotatably supported by the case 5 by a bearing device 8, and has a clutch gear 9 fixed to one end thereof.

Further, the case 5 rotatably supports an output shaft 11 on the same axis as the input shaft 4 by means of a bearing device 10, and a sleeve-shaped counter shaft 12 is provided below the output shaft 11 and parallel thereto. and an input shaft 3 of the sub-transmission device 30 disposed concentrically in the hollow portion of the counter shaft 12.
1 are rotatably supported by bearing devices 13 to 16, respectively. The counter shaft 12 collectively supports a first speed counter gear 17, a second distance counter gear 18, an overdrive counter gear 19, and a berth counter gear 20. The output shaft 11 also has a first purpose gear 21 that meshes with the first distance counter gear 17, a second distance gear 22 that meshes with the second distance counter gear 18, and an overdrive counter gear. 19 and an overdrive gear 23 that meshes with the gear 19. A first synchronizer 24 is provided between the clutch gear 9 and the overdrive gear 23, and a second synchronizer 25 is provided between the first gear gear 21 and the second distance gear 22. Each is provided. These synchronizers may be well-known synchronizers such as Borgwarner synchronizers, and when the hub sleeve of the first synchronizer 24 moves to the left in the figure, the input shaft 4 and the output shaft 11 are directly connected. When the top range of synchronization is achieved, the first synchronizer 2
When the hub sleeve of the second synchronizer 25 moves to the right in the figure, the overdrive gear 23 is fixedly connected to the output shaft 11 to achieve an overdrive range, and the hub sleeve of the second synchronizer 25 moves to the right in the figure. When the hub sleeve of the second synchronizer 25 moves to the left, the first far gear 21 is fixedly connected to the output shaft 11 to achieve the so-called first range, and when the hub sleeve of the second synchronizer 25 moves to the right in the figure. The second distance gear 22 is connected to the output shaft 1
A second range is achieved by being fixedly connected to 1. Further, the second synchronizer 25 has a reverse gear 26 in its hub sleeve, and this reverse gear 2
6, the reverse counter gear 20 is selectively engaged with the IJ reverse drag gear 26' shown in broken lines in the figure, and when this engagement is performed, the reverse gear is achieved. be done. The switching of the first and second synchronizers 24, 25 and the reverse idler gear 26' is effected by a manual shift lever 27 in a manner known per se. The input shaft 31 of the sub-transmission device 30 integrally has a gear 32 at one end thereof, which is always engaged with the clutch gear 9.

The sub-transmission device 30 has a sun gear shaft 33 on the same axis as the axis of the input shaft 31, and this sun gear shaft 33 has a sun gear 34 integrally therein. The outer circumference of the sun gear 34 shows a plurality of planetary pinions 35 that mesh with it.
The planetary pinion 35 is rotatably supported by a planetary carrier 36 fixedly connected to the other end of the input shaft 31. Also, on the outside of the planetary pinion 35, there is an IJ that is concentric with the sangya 34.
A ring gear 37 is provided, and this ring gear 37 meshes with each of the planetary pinions 35. The ring gear 37 is connected to the counter shaft 12 via a one-way clutch 38. Also, the drama change distance device 3
0 includes a brake device 39 that selectively fixes the sangya shaft 33 and a clutch device 40 that selectively connects the sangya shaft 33 and the ring gear 37.
The brake device 39 and the clutch device 40 are hydraulically actuated cylinder-piston devices (not shown);
Alternatively, it is selectively driven by a solenoid device or the like. The clutch device 40 is in a non-operating state, the brake device 39 is in an operating state, and the sangya shaft 33
When the rotational power of the input shaft 31 is fixed, the rotational power of the input shaft 31 is transmitted from the planetary carrier 36 to the counter shaft 12 through the planetary pinion 36 and the ring gear 37, which rotate around the sun gear 34, and the rotational speed thereof is increased. communicated. Achieve the Zōendan level. On the other hand, when the operation of the brake device 39 is released and the clutch device 40 is activated, the sangya shaft 33 and the ring gear 37 are connected, and the three sub-transmission devices are in a so-called direct connection state. At this time, the rotational power of the input shaft 31 is directly transmitted to the counter ball 12 without changing the rotational speed. When the input shaft 4 and the output shaft 11 are not directly connected in the first range and the second range, the rotational force of the input shaft 4 is transmitted to the input shaft 31 via the clutch gear 9 and the gear 32; The rotational power is further transferred to the sub-transmission device 30.
1 is transmitted to the counter shaft 12 via the sub-transmission device 30.
However, in the top range where the input shaft 4 and the output shaft 11 are directly connected, the rotational power of the input shaft 4 is directly transmitted to the output shaft 11, so that the rotational power of the input shaft 4 is directly transmitted to the output shaft 11.
No rotational power is transmitted to the gear 0, and the sub-transmission device 30 idles. FIG. 2 is a skeleton diagram showing another embodiment of the transmission according to the present invention.

In FIG. 2, parts corresponding to those in FIG. 1 are designated by the same reference numerals as in FIG. In this embodiment, the sun gear 34 of the sub-transmission device 30 is connected to the counter shaft 12.
The planetary carrier 36 integrally has a gear 41 that meshes with the clutch gear 9. The ring gear 37 is selectively fixed by a brake device 42, and the counter shaft 12 and the planetary carrier 36 are selectively connected by a clutch device 43. In this case, when the clutch device 43 is deactivated and the brake device 42 is activated to fix the ring gear 37, the rotational power transmitted from the input shaft 4 to the gear 41 via the clutch gear 9 is transferred to the planetary carrier 36, The rotational speed is increased and transmitted to the counter shaft 12 via the planetary pinion 35 and sangya 34. On the other hand, when the brake device 42 is deactivated and the clutch device 43 is activated,
By connecting the counter shaft 12 and the planetary carrier 36, the sub-transmission device 30 is brought into a directly connected state.
At this time, the rotational power applied to the gear 41 is directly transmitted to the counter shaft 12 without changing the rotational speed. Even in this embodiment, when the input shaft 4 and the output shaft 11 are in the top range where they are directly connected, the rotational power of the input shaft 4 is
Since the rotational power is directly transmitted to the output shaft 11, the rotational power is not transmitted to the dramatic transmission 30, and the auxiliary transmission 30 idles.

Thus, according to the present invention, it is possible to avoid transmitting unnecessary rotational power to the sub-transmission during the top range, which is most often used during normal driving conditions, and to extend the life of the sub-transmission. It will be appreciated that an improved transmission is obtained.

[Brief explanation of drawings]

FIG. 1 is a skeleton diagram showing one embodiment of the transmission according to the present invention, and FIG. 2 is a skeleton diagram showing another embodiment of the transmission according to the present invention. 1-engine, 2-clutch device, 3-transmission device, 4-
Input shaft, 5-case, 7-main transmission, 8-bearing device, 9-clutch gear, 10-bearing device, 11
~Output shaft, 12~Counter shaft, 13~16~Bearing device, 17~First distance counter gear, 18~Second distance counter gear, 19~Overdrive counter gear, 2
0 ~ counter gear for reverse, 21 ~ gear for 1st speed, 2
2 ~ 2nd speed gear, 23 ~ Overdrive gear, 24
~first synchronizer, 25~second synchronizer, 26~reverse gear, 26'~reverse idler gear, 27~manual shift lever, 30~auxiliary transmission,
31~Input shaft, 32~Gya, 33~Sangya axis, 34~
sangya, 35 ~ planetary pinion, 36 ~ planetary gear 1' gear, 37 ~ ring gear, 38 ~ one way clutch, 39 ~ brake device, 40 ~ clutch device, 4
1 - Gear, 42 - Brake device, 43 - Clutch device. Figure 1 Figure 2

Claims (1)

[Claims] 1 An input shaft, an output shaft disposed on the same axis as the input shaft, a counter shaft disposed parallel to the output shaft, and a planetary gear mechanism disposed on the same axis as the counter shaft. A sub-transmission device that transmits the rotational power given from the input shaft to the counter shaft at a speed ratio selected from a speed ratio of 1 and another finite value different from this, and carried by the counter shaft. and a gear that rotates concentrically with the countershaft and a gear that is carried by the output shaft and rotates concentrically with the output shaft, providing a gear train with a plurality of different speed ratios between the countershaft and the output shaft. a plurality of gears, a synchronizer that causes only one selected one of the plurality of gear trains to be in a driving force transmission state and the other gear trains to be in an idle rotation state that does not transmit driving force; the input shaft and the output shaft; A transmission device comprising a synchronizer that selectively connects directly to a shaft.