JPS61266852A - Gear transmission - Google Patents

Abstract

PURPOSE:To reduce the constituent parts by providing pairs of speed change gear couples between an input shaft arranged on the same axis as an output shaft via a clutch and a countershaft and also between the countershaft and the output shaft. CONSTITUTION:A pair of 1st to 3rd speed gear couple 6 and a pair of twin 5-speed gear couple 7 are provided between an input shaft 2 and a countershaft 4 of a gear transmission A, and a pair of high-speed stage gear couple 9 and a pair of low-speed stage gear couple 10 are provided between the countershaft 4 and an output shaft 3. Accordingly, by combining these gear ratios the change gear ratios of forward 5 stages can be obtained by the 4 pairs of gear couples 6, 7, 9 and 10. Further, since the final change gear ratio can be obtained by combining gear ratios, even the change gear ratio of low-speed stage with a large final change gear ratio can be obtained by combining gears having a small change gear ratio.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a gear transmission used as a transmission of an automobile or the like.

(Prior art) An example of a conventional gear transmission is shown in Figure 2.98 on page 87 of "Automotive Engineering Complete Book, Volume 9: Power Transmission Device" (published by Kinzankaido, November 1980). Something like this is known.

This conventional gear transmission is a 5 forward gear gear transmission and 1 reverse gear gear transmission (with 4 gears and 10 overtops), and has a subshaft configuration in which the input shaft and output shaft are arranged on the same shaft. A pair of drive gears fixed to the shaft are provided between the input shaft and the subshaft to transmit the driving force from the input shaft to the subshaft, and between the subshaft and the output shaft are provided a pair of driving gears for 1st speed and 2nd speed. , 3rd speed, and 5th speed transmission gear pairs.

Incidentally, the frequently used 4th speed is obtained by directly connecting the input shaft and the output shaft via a synchronization mechanism.

Further, the synchronization mechanism is provided on the output shaft between the first gear pair and the second gear pair, between the third gear gear pair and the driving gear pair, and between the fifth gear gear pair.

(Problems to be solved by the invention) However, in such a conventional gear transmission,
Based on a single reduction ratio by a drive gear pair, 1st speed, 2nd speed
In order to obtain a gear ratio of 5 forward speeds, as in the conventional example, the gear ratios of 3rd, 3rd, and 5th gears were obtained by pairs of transmission gears with different gear ratios. There was a problem that five pairs (10 gears) were required and the cost was high.

In addition, since it was necessary to install the low gear gears (1st gear and 2nd gear) with a large number of teeth and gear diameter on the output shaft side (even if you tried to install them on the input shaft or countershaft, it would be difficult to install them on the input shaft or subshaft). (The l-speed input gear rotates at a high speed during high-speed gears, etc., so it cannot be installed.), and the load on the synchronization mechanism (transmission mechanism) is large in low gears, requiring a large operating force when changing gears. There was a point.

In addition, since a pair of drive gears are provided that constantly mesh and drive as the input shaft rotates, there are many parts that rotate together with the input shaft even in the neutral state, which can cause problems due to engine rotation fluctuations such as when the engine is idling. There is a problem in that gear noise and vibration tend to increase.

(Means for Solving the Problems) The present invention has been made for the purpose of solving the above-mentioned problems, and in order to achieve this purpose, the present invention has been made in order to solve the above-mentioned problems. , the ratio of the gear ratios of 1st and 2nd gears (γ1/γ2), and the ratio of the gear ratios of 3rd and 5th gears (γ
3/γ5) are almost the same, and in a gear transmission equipped with an input shaft, an output shaft, and a subshaft arranged in parallel shafts, in which a speed change gear is provided, the input shaft and the output shaft can be directly connected via a clutch and arranged on the same shaft, and a pair of transmission gears that can select different gear ratios is provided between the input shaft and the subshaft, and between the subshaft and the output shaft. A pair of transmission gears are provided that allow selection of different gear ratios.

(Function) Therefore, in the gear transmission of the present invention, by using the above-mentioned means, there is provided a pair of transmission gears that are provided between the input shaft and the subshaft and can select different gear ratios; A transmission gear pair is provided between the subshaft and the output shaft and can select different gear ratios, and the transmission ratio is obtained by a combination of gear ratios. In this case, 4 different gear ratios can be obtained, and if the input shaft and output shaft are directly connected to each other by engagement of the clutch, the gear ratio of 5 forward gears can be obtained by 4 pairs of transmission gears (8 gears). gears).

In addition, since the final gear ratio can be obtained by combining the gear ratios, even if the gear ratio is in a low gear with a large final reduction ratio,
It can be obtained by combining gears with small reduction ratios,
Moreover, since the transmission mechanism can be provided on the input shaft side, the gear ratio and the moment of inertia around the shaft are reduced, and the gear can be shifted to a lower gear with a small operating force.

Additionally, in the neutral state, where no gear ratio is selected, it is possible to eliminate gears that mesh with and drive the input shaft, making it possible to eliminate gear noise and vibration caused by rotational fluctuations of the input shaft. .

(Example) Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

In describing this embodiment, an automatic Ichikawa gear transmission with five forward speeds and one reverse speed, in which the gears are changed by hydraulic pressure, will be taken as an example.

First, the configuration of the first embodiment will be explained.

What is shown in Fig. 1 is a gear transmission A for an automobile according to the first embodiment.
This first embodiment consists of a transmission case 1, an input shaft 2 degrees, an output shaft 3, a countershaft (secondary shaft) 4.4-speed clutch 5.1-3 speed gears pair 6, 2nd speed - 5th gear pair 7,
first synchronization mechanism 8, high speed gear pair 9, low speed gear pair 10,
A second synchronization mechanism 11 and a reverse gear train 12 are provided.

Mission case 1 includes each shirt (with parallel axis arrangement) 2, 3
．． 4 and a case that can store gears, each shirt) 2,
3.4 is bearing 12 for transmission case 1,
It is rotatably supported by 13, 14, and 15.

The input shaft 2 is a shaft into which rotational driving force from the crankshaft 16 of the engine is input via the clutch 17.

Note that as the clutch 17, a seat friction clutch, a torque converter/heater, or the like is used.

The output shaft 3 is a shaft that converts the rotation input to the input shaft 2 into rotation at a predetermined gear ratio and rotational direction according to the selected gear stage, and provides rotational driving force to the drive wheels.

The counter shaft 4 is a shaft provided with a counter gear used in each gear stage, and is arranged parallel to the input shaft 2 and the out/out shaft 3 on the same axis with a gap in between. .

The 4-speed clutch 5 is a clutch 4j provided between the input shaft 2 and the output shaft 3 which are arranged on the same axis, and when the clutch and the clutch are engaged, the input shaft 2 and the output shaft 3 are directly connected. A 4th speed gear ratio (=1) is obtained.

Note that this 4-speed clutch 5 is equipped with a hydraulic actuator' (
(not shown) is provided, and when the 4th gear is selected, the clutch member on the input shaft 2 side is moved to the right in the drawing (in the direction of arrow B)...notch engagement is performed. .

The 1st-3rd speed gear pair 6 includes a 1st-3rd speed gear 61 rotatably supported on the input shaft 2 and a 1st-3rd speed counter gear 6 fixedly provided on the countershaft 4.
2, and both gears 61 and 62 are provided in a constant meshing state.

The 2nd-5th speed gear pair 7 includes a 2nd-5th speed gear 71 rotatably supported on the input shaft 1-2, and a 2nd-5th speed gear 71 fixed to the countershaft 4. 72, and both gears 71.7
2 are provided in a constant meshing state.

The first synchronization mechanism 8 connects the input shaft 2 and the gears on the transmission side (1st-3rd gear 61 or 2nd gear) during a transmission operation.
After making the rotational peripheral speed equal to that of the speed-5th gear 71),
This is a mechanism for fixing the gear on the transmission side by meshing with the input shaft 2 in the rotational direction. set up ('j set up)

The first synchronizing mechanism 8 is provided with a hydraulic actuator (not shown), and when the first or third gear is selected, the sleeve of the first synchronizing mechanism 8 is moved toward the left side of the figure. (in the direction of arrow C), and when the second or fifth gear is selected, the sleeve is moved to the right in the drawing (in the direction of the arrow).

The high-speed gear pair 9 includes a high-speed gear 91 rotatably supported on the output shaft 3.

A high-speed stage counter gear 92 is fixedly provided on the counter shaft 4, and both gears 91.
92 are provided in a constantly engaged state.

□The low speed gear pair 10 includes a low speed gear 101 rotatably supported on the output shaft 3, and a low speed counter gear 10 fixedly provided on the counter shaft 4.
2, both gears 101, 10
2 are provided in a constant meshing state.

The second synchronization mechanism 11 is a mechanism provided between the output shaft 3 and the high speed gear 9 and the low speed gear 10, and has the same function as the first synchronization mechanism 8.

Note that this second synchronization mechanism 11 also includes a hydraulic actuator (
(not shown) is provided, and when the higher gear position (3rd or 5th gear) is selected, the sleeve of the second synchronizing mechanism 11 is moved to the left in the drawing (in the direction of arrow E),
When a high gear (1st or 2nd gear) on the lower gear side is selected, the sleeve is moved to the right in the drawing (in the direction of arrow F).

The reverse gear train 12 includes a reverse gear 121 fixedly provided on the input shaft 2 and a reverse counter gear 12 fixedly provided on the counter shaft 4.
2, and a reverse idler gear that is slidable in the axial direction on the idler shaft 18! 23.

The reverse idler gear 123 is provided with a hydraulic actuator (not shown), and when the reverse gear stage is selected, the reverse idler gear 123 is activated.
3 to the right in the drawing (in the direction of arrow G), and is engaged with the reverse gear 121 and the reverse counter gear 122.

Next, the number of teeth of the forward gear of the first embodiment and each gear pair 6
,7,9. The IO gear ratios ia, ib, jc, and id were set as shown in Table 1 below.

Table 1 Next, the operation of the first embodiment will be explained.

(a) When in neutral When in neutral, the hydraulic actuator does not operate and no power is transmitted from the input shaft 2 to the output shaft 3.

The only members that rotate during this neutral state are the first synchronizing mechanism 8 provided on the input shaft 2, a part of the clutch member of the 4-speed clutch 5, and the reverse gear 121, and none of the gear pairs mesh with each other. Never drive.

(b) At the 1st speed, the 1st-3rd gear 61 is fixed to the input shaft 2 and the lower gear 101 is fixed to the output shaft 3 by the hydraulic actuator.

Therefore, the power transmission path at 1st speed is input shaft 2 → first synchronization mechanism 8 → 1st-3rd gear 61 → 1st-3rd gear counter gear 62 → counter shaft 4 → low-speed counter gear 102 → low-speed gear Gear 101 → second synchronous mechanism 11 →
This will be the output shaft 3.

Note that the gear ratio yt (=iaXid) at 1st speed is 3.
It becomes 550.

(c) At 2nd speed, the hydraulic actuator
The fifth speed gear 71 is fixed to the input shaft 2, and the low speed gear 101 is fixed to the output shaft 3.

Therefore, the power transmission path at 2nd speed is input shaft 2 → first synchronization mechanism 8 → 2nd-5th gear 71 → 2nd-5th gear counter gear 72 → counter shaft 4 → low-speed counter gear 102 → low-speed gear Gear 101 → second synchronous mechanism 11 →
This will be the output shaft 3.

Note that the gear ratio γ2 (=ibXid) at 2nd speed is 2.
It becomes 040.

(iv) 3rd speed In 3rd speed, the l-3rd gear 61 is fixed to the input shaft 2 and the high speed gear 91 is fixed to the output shaft 3 by the hydraulic actuator.

Therefore, the power transmission path in 3rd gear is input shaft 2 → first synchronization mechanism 8 → 1st to 3rd gear 61 → 1st-3rd gear counter gear 62 → counter shaft 4 → high speed counter gear 92 → high speed gear Gear 91-+second synchronization mechanism 11→output shaft 3.

In addition, the gear ratio y3 (= i aX i c
) becomes 1.407.

(e) 4th gear In 4th gear, the 4th gear clutch 5 is engaged by the hydraulic actuator, and the rotational driving force from the input shaft 2 is transmitted as is to the output shaft 3, and the gear ratio γ4 is 1.000. Become.

(f) 5th speed In 5th speed, the 2nd-5th speed gear 71 is fixed to the input shaft 2 and the high speed gear 91 is fixed to the output shaft 3 by the hydraulic actuator.

Therefore, the power transmission path at 5th speed is input shaft 2 → first synchronization mechanism 8 → 2nd-5th gear 71 → 2nd-5th gear counter gear 72 → counter shaft 4 → high-speed counter gear 92 → high-speed Step gear 91 → second synchronous mechanism 11 → output shaft 3.

In addition, the gear ratio 75 (=ibXic) at 5th gear is 0.
842, and the rotational driving force from the input shaft 2 is accelerated.

(g) When reversing When reversing, use a hydraulic actuator. The reverse idler gear 123 is moved in the direction of arrow G, and the low speed gear 101 is fixed to the output shaft 3.

Therefore, the power transmission path when reversing is input shaft 2 → reverse gear 121 → reverse idler gear 123.
→Reverse counter gear 122→Counter shaft 4→
Low speed counter gear 102 → low speed gear 101 → second synchronization mechanism 11 → output shaft 3.

In addition, when moving backward, by adding the reverse idler gear 123, a rotational driving force in the opposite direction to that in the forward gear is outputted from the output shaft 3.

As described above, in the first embodiment, the gear pair 6.7 on the input shaft z side and the output shirt)
By combining the gear ratios of gear pairs 9 and 10 on the 3rd side, the gear ratio of the 5 forward gears is changed to 4 pairs of gears 6, 7, and 9.10.
(8 gears), and its speed ratio can be set to almost the same value as a general manual gear transmission with 5 forward speeds.

In addition, since the final gear ratio can be obtained by combining gear ratios, even in low gears (1st and 2nd gears), it can be obtained by combining gears with small reduction ratios. 8 can be provided on the input shaft z side, the gear ratio and the moment of inertia around the axis are reduced, and the gear can be shifted to a lower gear with a small operating force.

Note that the ability to reduce this operating force has the advantage that when the actuator is operated using hydraulic pressure, negative pressure, a solenoid, or the like, the gear shift operation can be performed without requiring a high-output device.

Furthermore, since there is no gear that engages with and drives the input shaft 2 when in neutral, it is possible to eliminate gear noise and vibration caused by engine rotational fluctuations when the engine is idling.

Next, a second example will be described.

In this embodiment, as shown in FIG. 2, a high speed gear 91 of a high speed gear pair 9 and a low speed gear 10 of a low speed gear pair 10 are used.
1 is fixed to the output shaft 3, a high speed counter gear 92 is provided on the counter shaft 4 via a high speed clutch 19, and a low speed counter gear 102 is provided on the counter shaft 4 via a low speed clutch 20 and a one-way clutch 21. This is a gear transmission A' for an automobile.

In addition, the high speed clutch 19 and the low speed clutch 20 include the following:
A hydraulic actuator (not shown) is provided.

Further, since the other configurations are the same as those in the first embodiment, the same reference numerals are attached to the drawings and explanations thereof will be omitted.

The operation of the second embodiment will be explained.

Regarding the speed change operation, the difference is that instead of the second synchronizing mechanism 11 of the first embodiment, the high speed clutch 19 and the low speed clutch 20 are engaged by a hydraulic actuator, and the low speed clutch 20 is engaged in the first or second speed. is engaged, and the high-speed clutch 19 is engaged in third or fifth gear.

Furthermore, by providing the one-way clutch 21,
Even if oil pressure to the low gear clutch zO cannot be obtained, 1
When speed or second speed driving is possible and drive is transmitted via the one-way clutch 21, so-called engine braking is not activated during coasting, which is driving by inertia, improving fuel efficiency.

Further, by providing the one-way clutch 21, the hydraulic actuator that operates the high-speed clutch 19 and the low-speed clutch 20 can use hydraulic pressure driven by the output shaft 3 or countershaft 4, or hydraulic pressure from a pump. .

Note that other functions are the same as those in the first embodiment, so explanations will be omitted.

Although the embodiments of the present invention have been described above in detail with reference to the drawings, the specific configuration is not limited to these embodiments, and the present invention may be modified without departing from the gist of the present invention. included.

For example, in the embodiment, a gear transmission is shown in which the gear shift operation is performed by hydraulic pressure, but it may also be performed by other means such as negative pressure or a renoid, or manually. good.

In addition, in the embodiment, a gear transmission that can obtain four speed ratios was shown, but by increasing the number of gear pairs on the input shaft side and the gear pairs on the output shaft side, for example, the number of gear pairs on the input shaft side can be increased to two pairs. , the number of gear pairs on the output shaft side may be three, and six gear ratios can be obtained.

Further, in the first embodiment, a transmission mechanism using only a synchronizing mechanism is shown, but a transmission mechanism using a fastening means such as a multi-disc clutch may be used.

(Effects of the Invention) As explained above, in the gear transmission of the present invention, the input shaft and the output shaft can be directly connected via the clutch and are arranged on the same shaft, and the input shaft and the sub-shaft are arranged on the same shaft. A pair of transmission gears that can select different gear ratios is provided between the subshaft and the output shaft, and a pair of transmission gears that can select different gear ratios are provided between the subshaft and the output shaft. A large number of transmission ratios can be obtained by pairing.

In addition, since the gear ratio can be obtained by combining the gear ratios,
It is possible to reduce the load on the transmission mechanism without requiring a large gear ratio setting.

Furthermore, when no speed ratio is selected, it is possible to eliminate gears that mesh with and drive the input shaft, making it possible to eliminate gear noise and vibration caused by rotational fluctuations of the input shaft.

[Brief explanation of drawings]

FIG. 1 is a skeleton diagram showing a gear transmission for an automobile according to a first embodiment of the present invention, and FIG. 2 is a skeleton diagram showing a gear transmission for an automobile according to a second embodiment.

Claims (1)

[Claims] 1) In a gear transmission equipped with an input shaft, an output shaft, and a subshaft arranged in parallel shafts in which a speed change gear is provided, the input shaft and the output shaft can be directly connected via a clutch and are arranged on the same axis, A gear transmission characterized in that a pair of transmission gears capable of selecting different gear ratios is provided between an input shaft and a subshaft, and a pair of transmission gears capable of selecting a different gear ratio are provided between a subshaft and an output shaft. .