JPS62242165A - Transmission for vehicle - Google Patents

Abstract

PURPOSE:To make a car travelable with one side route when the other side gets out of order, by connecting respective output shafts via the clutch installed at the one end side of an input shaft of a manual transmission as well as via the sub-transmission installed at the other end side, and installing a one-way clutch between both routes. CONSTITUTION:At the time of starting a vehicle, engine power is transmitted to a front cover 10 of a hydraulic coupling, and a pump impeller 12 is rotated, but since a clutch 15 is opened, rotation is transmitted to a turbine runner 13 whereby an input inner shaft 1 of a manual transmission 3 is rotated. At this time, since a brake 33 of a sub-transmission 5 is engaged, a sun gear 35 is locked by operation of a one-way clutch 32 so that rotation of the input inner shaft 16 is transmitted to a ring gear 37 and a pinion 36 and decelerated, then it is transmitted to an input outer shaft 17, outputted to an output shaft 23 via the gear train G1 of the transmission 3. Here, even if a power input route for either of a route of the clutch 15 or a route of the sub-transmission 5 gets out of order, a car is travelable with the other side power input route.

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a manual transmission or a semi-automatic transmission consisting of a hydraulic coupling that automates a starting operation and a manual transmission, in which an auxiliary transmission is connected to the manual transmission. The present invention relates to a vehicle transmission.

[Conventional technology]

Conventionally, a vehicle transmission in which an auxiliary transmission is connected to a manual transmission is disclosed in, for example, Japanese Patent Application Laid-Open No. 60-30849. This is a vehicular transmission in which a manual transmission is connected to an engine via a transmission clutch, and an auxiliary transmission equipped with a two-stage transmission system, high and low, is installed in series with the manual transmission, and the auxiliary transmission has a high-speed A hydraulic clutch is intervened in the transmission system, and a one-way clutch that allows over-rotation on the output side is intervened in the low-speed transmission system, and the low-speed transmission system is established when the hydraulic clutch is released, and the high-speed transmission system is established when the hydraulic clutch is engaged. This is how it was done.

In addition, in a semi-automatic transmission, a manual transmission is connected to the engine via a fluid coupling, the starting operation is automatically performed by the fluid coupling, and the gear change is performed by the manual transmission.
This is done manually according to the driver's intention or driving conditions.

[Problem that the invention seeks to solve]

In a transmission equipped with an auxiliary transmission equipped with a transmission system with two high and low stages in series with the manual transmission described above, since the hydraulic clutch and the auxiliary transmission are arranged in series with the manual transmission, either one There was a problem that if the machine broke down, it would become impossible to drive. Furthermore, since the power transmission shaft of the auxiliary transmission passes through the gear shaft, increasing the capacity of the power transmission shaft causes the problem that the gear becomes larger and lacks compactness.

Furthermore, the semi-automatic transmission described above has a problem in that the driver must frequently change gears while the vehicle is running so as to adjust the gear position to each situation. Furthermore, when the number of gears is increased in order to improve power performance or fuel efficiency, the transmission itself becomes larger, and the driver has to perform gear shifting operations frequently. As a result, this has been a major hindrance to improving power performance or fuel efficiency. The present invention solves the above problems, enables smooth gear shifting, simplifies gear shifting operation, and improves power efficiency. The purpose of the present invention is to provide a vehicle transmission that can improve performance and fuel efficiency.

[Means for solving problems]

To this end, the vehicle transmission of the present invention includes a manual transmission and an auxiliary transmission connected to the manual transmission, in which a clutch is disposed on one end side of the input shaft of the manual transmission. The output shaft of the engine is connected to one end of the input shaft through the clutch to form a first power transmission path, and the sub-transmission is disposed on the other end side of the input shaft, and the sub-transmission connecting the output shaft of the engine to the other end of the input shaft to form a second power transmission path, and disposing a one-way clutch that only allows relative rotation in a predetermined direction between both power transmission paths. Accordingly, the present invention is characterized in that it is possible to shift into two high and low gears simply by engaging and disengaging the clutch.

[Action and effect of the invention]

In the present invention, power can be transmitted from the engine 1 from both the front and the rear of the manual transmission 3, and the auxiliary transmission 5 enables two high and low gear shifts, and over-rotation of the input shaft is prevented. The one-way clutch allows for shifting with less shock.

Therefore, by automating a part of the gear shifting operation using a one-way clutch and auxiliary transmission, the complexity of gear shifting operation can be reduced.Also, there are two power input systems to the manual transmission, one from the front and one from the rear. The number of gears can be doubled, making multi-stage shifting possible, and even if one of the power input systems breaks down, the vehicle can be driven using the other power input system. In addition, by increasing the number of gears, it is possible to improve power performance and fuel efficiency, and by adopting existing gear mechanisms for conventional manual and semi-automatic transmissions, design costs can be significantly reduced. be able to. Furthermore, in the case of a semi-automatic transmission using a fluid coupling, smooth starting and shifting with less shock are possible, and since the clutch can also be used as a lock-up clutch, the entire system can be made more compact.

〔Example〕

Examples will be described below with reference to the drawings.

FIG. 1 is a diagram for explaining one embodiment of the present invention, FIG. 2 is a sectional view showing a specific configuration example of FIG. 1, and FIG. 3 is a diagram showing another specific configuration example of FIG. 1. 4 is a diagram for explaining another embodiment of the present invention, FIG. 5 is a sectional view showing a specific configuration example of FIG. 4, and FIG. 6 is a diagram for explaining another example of the configuration of FIG. 7 and 8 are cross-sectional views showing a configuration example, and are diagrams for explaining other embodiments of the present invention.

In the figure, 1 is an engine, 2 is a fluid coupling, 2a is a speed change clutch, 3 is a manual transmission, 5 is an overdrive mechanism,
6 is a differential gear, 7 is a drive wheel, 9 is a crankshaft, 10 is a front cover, 11 is a rear cover, 12 is a pump impeller, 13 is a turbine runner, 14 is a one-way clutch, 15 is a clutch, 16 is an input inner shaft, 17 is Input outer axis,
19 is the transmission case, 20 is the human power shaft, 21 is the input gear of the differential gear, 22 is the output gear, 23 is the output shaft, 25 is the first
A switching clutch, 26 is a second switching clutch, 27 is a drive gear, 29 is a driven gear, 30 is a shift gear, 31 is a planetary gear device, 32 is a one-way clutch, 33 is a brake mechanism, 34 is a piston, 35 is a sun gear, 36 is a 37 is a ring gear, 39 is a carrier, 40 is a rotating ring, and G1, G2, G3, G4, and GR are gear trains.

1 and 2, the vehicle transmission of the present invention is constructed by connecting a manual transmission 3 to an engine 1 via a fluid coupling 2, and connecting an auxiliary transmission 5 to the manual transmission 3. , the output from the manual transmission 3 is transmitted to the drive wheels 7 of the vehicle via the differential gear 6. The fluid coupling 2 is a front cover lO1 connected to the crankshaft 9 of the engine 1.
and a rear cover 11, and a front cover 10.
A pump impeller 12 is disposed on the inner wall of the pump, and a turbine runner 13 is disposed opposite the pump impeller 12. Further, a latch 1 is provided between the rear cover 11 and the turbine runner 13, which can be frictionally engaged with the rear cover 11.
A turbine runner 13 is coupled to transmit power to an input inner race 16 of a manual transmission 3, which will be described later, and a clutch 15 transmits power to an input outer shaft 17 of a manual transmission 813. are combined like this. The clutch 15 also serves as a conventional lock-up clutch.

The manual transmission 3 is configured, for example, as a two-shaft parallel gear mechanism with four forward speeds and one reverse speed. 20
and an output gear 22 that meshes with the input gear 21 of the differential gear 6.
A forward gear train G1, G2, G3, G4 and a reverse gear train are provided between the input shaft 20 and the output shaft 23 in parallel with each other. GR
has been set up. Further, the input shaft 20 is connected to the human-powered inner ring 1
6 and an input outer shaft 1 fitted to the outside of the cough input inner ring 16
7, and the input inner ring 16 is composed of the turbine runner 1
3 so as to transmit power thereto, and the input outer shaft 1
7 is connected to the clutch 15 so that power is transmitted thereto.

Further, on the output shaft 23, first and second gear trains G1 and G2 are provided.
A synchromesh type first switching clutch 25 is provided between the input shaft 20 and the third and fourth gear trains G3.
04, the synchromesh type second switching clutch 26
are provided, and each gear train G1, G2,
G3 and G4 are selected. The reverse gear train GR includes a drive gear 27 on the input shaft 20, a driven gear 29 integrally formed with the first switching clutch 25, and an intermediate shift gear 30.
(FIG. 1), and by switching the shift gear 30 to the right reverse position in the drawing, the driving gear 27 and the driven gear 29 are connected via the shift gear 30.

The sub-transmission 5 includes a planetary gear unit 31, a one-way clutch 32, and a brake 33. A sun gear 35 of a planetary gear device 31 is rotatably supported on the input inner ring 16 of the manual transmission a3, and a one-way clutch 32 is connected to the outer periphery of the cough sun gear 35. , piston 3
A brake 33 operated by the brake 3 is provided.
3 and one-way clutch 32 are engaged and released, sun gear 35 is configured to be fixed or rotatable. In addition, the input inner shaft 16 is equipped with a planetary gear system ff31.
A ring gear 37 that meshes with a pinion 36 is coupled,
The pinion 36 meshes with the sun gear 35.

On the other hand, a carrier 39 of a planetary gear device 31 is coupled to the input outer shaft 17 of the manual transmission 3, and the carrier 39 rotatably supports a pinion 36.

The clutch 15 and brake 33 described above are automatically controlled by a hydraulic control device, and for example, they may be controlled by hydraulic pressure corresponding to the rotation speed of the drive pinion, or the hydraulic pressure may be controlled by iris by an electronic control device. good.

Next, the operation of the present invention having the above configuration will be explained. When the vehicle starts, the clutch 15 of the fluid coupling 2 is released, and the first switching clutch 25 of the manual transmission 3 is released.
The gear train G1 for the first forward speed is selected, and the brake 33 of the sub-transmission 5 is engaged. engine l
The power is transmitted to the front cover 10 of the fluid coupling 2 via the crankshaft 9, causing the pump impeller 12 to rotate, but since the clutch 15 is released, the rotation of the pump impeller 12 is transmitted to the turbine runner 13. , the input inner shaft l of the manual transmission 3 connected thereto rotates. At this time, since the brake 33 of the sub-shift [5] is engaged, the sun gear 35 of the planetary gear set 31 is fixed by the operation of the one-way clutch 32, so that the rotation of the input inner shaft 16 is controlled by the ring gear 37, Binion 36
0 is transmitted to the input outer shaft 17 via the carrier 39, is decelerated by the relationship between the numbers of gears of the ring gear 37 and the binion 36, and is then transmitted to the input outer shaft 17 through the carrier 39.
The clutch 1 in the fluid coupling 2 is output to the output shaft 23 equipped with the output gear 22 via the gear train G1 for speed.
When clutch 15 is engaged, the power of engine 1 is transferred to clutch 15.
The rotation of the input outer shaft 17 is directly transmitted to the input outer shaft 17 via the carrier 39 of the planetary gear set 31.
, is transmitted to the sun gear 35 via the pinion 36, the rotational speed of the input outer shaft 17 becomes approximately equal to the rotational speed of the input inner ring 16, the sun gear 35 also rotates at approximately the same rotational speed, and due to overrotation of the one-way clutch 32, the input Power transmission from the inner shaft 16 is cut off, allowing gear changes without releasing the brake 33.

Next, each gear train G1, G2, G3 in the manual transmission 3
, G4, the clutch 15 and brake 33 are released under interlock control with a shift lever (not shown) to create a neutral state, and the gear trains G1, G2, G3, and G4 are switched. and,
As mentioned above, immediately after changing the gear train, the manual shift 83
The rotation of the input inner ring 16 is decelerated by the planetary gear device 31, and then the input gears G1, G2,
The power of the engine L is directly transmitted to the input outer shaft 17 via the clutch 15. Then, due to overrotation of the one-way clutch 32, power transmission from the low-speed transmission wheels 16 is cut off, and the brake 3
3 (shifting is performed), it is possible to shift with less shock.Also, even if clutch 15 is released during downshifting, engine braking will not work at low speeds due to the action of one-way clutch 32. Therefore, the occurrence of shift shock is also suppressed.

The above operations are summarized in the table below.

In the figure, C is the direct clutch 15, B is the brake 33, F is the one-way clutch 32, ○ is activated, × is not activated,
The Δ mark indicates whether it is activated or not activated.

Therefore, by adding a speed reduction mechanism to a transmission with four forward speeds, it becomes possible to shift the speed through eight forward speeds.

FIG. 3 shows another specific configuration example in FIG. 1. The difference from the specific configuration example in FIG. 2 is that in FIG. However, in this embodiment, the piston 34 of the brake 33 is disposed within the outer peripheral space of the ti star gear device 31.
It is a point arranged in the outer peripheral space of. Thereby, the length of the transmission in the axial direction can be shortened, and the entire transmission can be made compact.

Next, the embodiment shown in FIGS. 4 to 6 will be explained. The difference from the embodiment shown in FIG. 1 is that in the embodiment shown in FIG. In contrast to underdrive output, this example
The main difference is that the direct power from the engine is output through overdrive in the auxiliary transmission.

4 and 5, the fluid coupling 2 has a front cover 10 connected to the crankshaft 9 of the engine 1 and a rear cover 11, and a pump impeller 12 is disposed on the inner wall of the rear cover 11. At the same time, a turbine runner 13 is arranged opposite to the pump impeller 12. Further, the turbine runner 13 is coupled to an input outer shaft 17 of a manual transmission 3 (described later) via a clutch 15 and a one-way clutch 14 that are automatically controlled by hydraulic pressure, and the front cover 10 is connected to a damper. It is connected to the input inner shaft 16 of the manual transmission 3 via 18 so that power is transmitted thereto.

Further, the sub-transmission 5 includes a planetary gear device 31 and a brake mechanism 33, and includes an input inner ring 16 of the manual transmission 3.
A carrier 39 of the planetary gear device 31 is spline-coupled, a pinion gear 36 is pivotally supported by the carrier 39, and the pinion gear 36 is meshed with a sun gear 35 and a ring gear 37. The sun gear 35 is rotatably supported by the input inner ring 16, and a rotary ring 40 is spline-coupled to the outer periphery of the sun gear 35, and a brake actuated by the piston 34 is attached to the outer periphery of the rotary ring 40. A mechanism 33 is provided, and the sun gear 35 is configured to be fixed or rotatable by engaging and releasing the brake mechanism 33. On the other hand, manual transmission 3
The pinion 36 of the planetary gear device 31 is connected to the input outer shaft 17 of the
A ring gear 37 that meshes with is connected.

Next, the operation of the present invention having the above configuration will be explained. The power of the engine l is constantly transmitted to the input inner ring 16 of the manual transmission 3 via the front cover 10 and damper 18, but when the clutch 15 is released, , brake mechanism 3
When the sun gear 35 is released due to the non-operation of the gear 3, it is in a neutral state. When starting the vehicle, the clutch 15 of the fluid coupling 2 is engaged, the first switching clutch 25 of the manual transmission 3 selects the single forward gear train G1, and the brake mechanism 33 is activated. The sun gear 35 is released. Therefore, the power of the engine 1 is transmitted to the rear cover 11 of the fluid coupling 2 and the pump impeller 12 via the crankshaft 9, and then the rotation of the pump impeller 12 is transmitted to the turbine runner 13.
, the input outer shaft 17 of the manual transmission 3 connected thereto rotates, and the gear train G for one forward gear of the manual transmission 3 is transmitted.
1 to an output shaft 23 having an output gear 22. On the other hand, the power of engine 1 is the front cover IO,
Although it is constantly transmitted to the input inner shaft 16 of the manual transmission 3 via the damper 18, since the brake mechanism 33 of the auxiliary transmission 5 is not operating, the sun gear 35 of the planetary gear unit 31
is released, and the rotation of the input inner shaft 16 is not transmitted to the ring gear 37 and is not transmitted to the human-powered outer shaft 17.

Next, when the brake mechanism 33 of the overdrive mechanism 5 is engaged, the sun gear 35 is fixed.
The rotation of 6 is transmitted to the ring gear 37 via the carrier 39 and the binion 36 of the planetary gear set 31, the speed is increased depending on the relationship between the numbers of gears of the binion 36 and the ring gear 37, and the rotation is transmitted to the input outer shaft 17. And ring gear 3
7, the rotational speed of the input outer shaft 17 exceeds the rotational speed of the turbine runner 13, and the one-way clutch 14
is idling, power transmission from the turbine runner 13 is cut off, and smooth gear shifting is possible.

In addition, each gear train C1, G2, G in the manual transmission 3
3. When switching to G4, the clutch 15 and brake mechanism 3 are controlled in conjunction with a shift lever (not shown).
By releasing the brake 33, a neutral state is created and each gear train G1, G2, G3, G4 is switched.As mentioned above, when the brake 33 is released, the power of the engine 1 is switched. An input is made from the front of the manual transmission 3 via the input outer shaft 17, and each gear train G1, G2,
When transmitting the power to G3 and G4 and engaging the brake 33, the power of the engine 1 is transferred from the rear of the manual transmission Ja, 3 to the input outer shaft 17 via the input inner sleeve 16 and the auxiliary transmission 5.
It is intended to be transmitted to

Since the one-way clutch 14 allows over-rotation of the input outer shaft 17, it is possible to shift gears with less shock. Furthermore, during a downshift when the brake 33 is released, the engine brake is not applied due to the action of the one-way clutch 14, so the occurrence of shift shock is also suppressed.

Therefore, by adding an auxiliary transmission to a transmission with four forward speeds, it becomes possible to shift through eight forward speeds.

5 and 6 show specific configuration examples in FIG. 4, and in FIG. 5, the piston 34 of the brake mechanism 33 is disposed within the outer peripheral space of the rear end of the input shaft 20. However, in FIG. 6, the piston 34 of the brake 33 is disposed in the outer peripheral space of the planetary gear device 31. Thereby, the length of the transmission in the axial direction can be shortened, and the entire transmission can be made compact.

FIGS. 7 and 8 show an embodiment of a vehicle transmission in which a manual transmission is connected to an engine via a gear shifting clutch without using a fluid coupling, in which an auxiliary transmission is connected to the manual transmission. ing.

7 is different from the embodiment shown in FIG. 4 in that a speed change clutch 2a is used instead of the fluid coupling 2, and FIG. 8 is different from the embodiment shown in FIG. The difference is that .

It should be noted that the present invention is not limited to the above-mentioned embodiments, and it goes without saying that various modifications can be made, and various combinations of 8-speed shifting methods can be considered.

As is clear from the above description, the present invention provides the following effects.

(a) Since a part of the gear shifting operation is automated using a one-way clutch and an auxiliary transmission, the complexity of the gear shifting operation can be reduced.

(b) Since there are two power input systems to the manual transmission, one from the front and one from the rear, the number of gears can be doubled, making multi-speed shifting possible, and one of the power input systems can fail. However, it is possible to run the vehicle using another power input system.

(c) By increasing the number of gears, it is possible to improve power performance and fuel efficiency.

(d) By employing an existing gear mechanism in conventional manual transmissions and semi-automatic transmissions, multi-stage transmission is possible, and design costs can be significantly reduced.

(E) In the case of a semi-automatic transmission that uses a fluid coupling, smooth starting and shifting with less shock are possible, and the direct coupling clutch can also be used as a lock Kenop clutch, making the entire system more compact. Become.

[Brief explanation of drawings]

FIG. 1 is a diagram for explaining one embodiment of the present invention, FIG. 2 is a sectional view showing a specific configuration example of FIG. 1, and FIG. 3 is a diagram showing another specific configuration example of FIG. 1. 4 is a diagram for explaining another embodiment of the present invention, FIG. 5 is a sectional view showing a specific configuration example of FIG. 4, and FIG. 6 is a diagram for explaining another example of the configuration of FIG. 7 and 8 are cross-sectional views showing a configuration example, and are diagrams for explaining other embodiments of the present invention. ■... Engine, 2... Fluid coupling, 2a... Shift clutch, 3... Manual transmission, 5... Overdrive mechanism, 6... Differential gear, 7... Drive wheel, 9・
...Crankshaft, 10...Front cover, 11...
・Rear cover, 12... Pump impeller, work 3...
Turbine runner, 14... One-way clutch, 15
...Clutch, 16...Input inner shaft, 17...Input outer shaft, 19...Transmission case, 20...Input shaft, 2
1... Input gear of differential gear, 22... Output gear, 2
3... Output shaft, 25... First switching clutch, 26...
...Second switching clutch, 27...Drive gear, 29...
・Followed gear, 30...Shift gear, 31...'ii
Star gear device, 32...One-way clutch, 33...
・Brake mechanism, 34... Piston, 35... Sun gear, 36... Binion, 37... Ring gear, 3
9...Carrier, 40...Rotating ring, G1, G2
, G3, G4, GR...gear train. Fig. 1 sj I + chance + s, j) % tsushi... 16 man-powered inner shaft 1'l outer shaft 3i washiri, 1 hura 1 minute ox figure Jiha Uke LL Iso 14wa, Waikura 1. Soup 15 Kura-n-go 1G λ force inner axis 17 person force outer axis Fig. 7

Claims (8)

[Claims] (1) In a vehicle transmission comprising a manual transmission and an auxiliary transmission connected to the manual transmission, a clutch is disposed at one end of the input shaft of the manual transmission, and the engine is connected to the engine via the clutch. connecting the output shaft of the first input shaft to one end of the input shaft.
a power transmission path, the auxiliary transmission is disposed on the other end side of the input shaft, and the output shaft of the engine is connected to the other end of the input shaft via the auxiliary transmission, thereby transmitting a second power. What is claimed is: 1. A vehicle transmission characterized in that a one-way clutch is provided that allows only relative rotation in a predetermined direction between both power transmission paths. (2) The vehicular transmission according to claim 1, wherein the sub-transmission includes a planetary gear set and a brake for fixing or releasing a sun gear of the planetary gear set. (3) The vehicle transmission according to claim 1, wherein the one-way clutch is connected in series with the clutch. (4) The vehicle transmission according to claim 2, wherein the one-way clutch is connected in series with the brake. (5) The vehicle transmission according to any one of claims 1 to 4, wherein the sub-transmission is connected to the engine via a fluid coupling. (6) The vehicle transmission according to any one of claims 1 to 4, wherein the clutch is connected to the engine via a fluid coupling. (7) The vehicle transmission according to any one of claims 2 to 6, characterized in that a piston for operating the brake is disposed in an outer peripheral space of an axial end of the input shaft. . (8) The semi-automatic transmission for a vehicle according to any one of claims 2 to 6, wherein a piston for operating the brake is disposed in an outer circumferential space of the planetary gear device.