JPS62220746A - Parallel-shaft type automatic transmission - Google Patents

Abstract

PURPOSE:To easily perform a speed change control eliminating even the necessity for forming a transmission into a large size or increasing its cost, by additionally providing a necessary number of one-way clutches corresponding to speed change shifts and one mechanical clutch and performing all the speed change controls through the one-way clutch. CONSTITUTION:The n-th-m-th speed shift gears 18, 16 in the side of an input shaft 10 can be connected with and disconnected from the input shaft 10 by their respective hydraulic clutches C2, C3, and the n-th-m-th speed shift gears 26, 24 in the side of an output shaft 11 are connected in series successively with one-way clutches OWC2, OWC3. And the n-th speed shift gear 26 of the output shaft 11 can be connected with and disconnected from the output shaft 11 through a reversing hydraulic clutch C4, while the m-th speed shift one-way clutch OWC3 can be connected with and disconnected from the output shaft 11through a mechanical clutch DC2. Accordingly, all the speed change controls can be performed interposing the one-way clutch to exist by additionally providing a necessary number of one-way clutches OWC2, OWC3 and one mechanical clutch DC2, and the speed change control can be easily performed with no necessity for forming a transmission into a large size and increasing its cost.

Description

[Detailed description of the invention] (b) Industrial application field The present invention relates to a parallel shaft automatic transmission.

(B) Conventional technology A conventional parallel shaft automatic transmission 'C' is, for example,
There is one shown in Publication No. 9-208263. This parallel shaft automatic transmission is designed to provide four forward gear ratios by combining four pairs of gears, four hydraulic clutches, and one one-way clutch.

(c) Problems to be solved by the invention However, such conventional V-shaft automatic transmissions do not have the following problems:
Only the first one-way clutch is provided, and shifting other than 1-2 requires releasing one hydraulic clutch and simultaneously engaging the other hydraulic clutch, making it difficult to perform smooth gear shifts. The problem is that it is relatively difficult. The present invention aims to solve these problems.

(d) Means for solving the problem The present invention adds a necessary number of one-way clutches according to the gear position and one mechanical clutch, thereby making all gear changes via one-way clutches. This solves the problem in item L. That is, in the parallel shaft automatic transmission according to the present invention, the nth shaft on the first shaft (human power shaft 10) side
The gears (2nd speed manual gear 18 and 3rd speed manual gear 16) for speed to mth speed (n and m are natural numbers where m > n) are for nth speed to mth speed, respectively. Hydraulic clutches (second oil JB clutch C2 and third hydraulic clutch C3)
), and the gears for the nth to mth speeds (the second gear output gear 26 and the third output gear 24) on the second shaft (output shaft 11) side are One-way clutch (OWC) for n-speed to m-th speed
2 and 0WC3'), and the nth speed gear (26) on the second shaft is connected to the reverse drive hydraulic clutch (
It can be connected to or disconnected from the second shaft via the fourth clutch C4), and the m-th speed one-way clutch (OWC3) is connected to the second shaft via the mechanical clutch (dog clutch DC2).
It can be connected to or separated from the shaft. Note that the symbols in parentheses indicate corresponding members in the embodiments described below in the case where n=2 and m=3.

(E) Operation If engine braking is not required, the m-th speed one-way clutch may be connected to the second shaft by a mechanical clutch. When the nth speed clutch is engaged in this state, the nth speed gear on the first shaft side, the nth to mth speed gears on the second shaft side, and the nth speed gear interposed between them. for ~ mth
The rotational force is transmitted to the second shaft via a one-way clutch for speed and a mechanical clutch. This allows the nth
It becomes a fast state. Next, when only the (n+1)th continuous hydraulic clutch is engaged, the rotational force on the first shaft side is generated by the (n-1st continuous hydraulic clutch), the (n-1st gear) to the mth gear gear on the second shaft side, and these. It is transmitted to the second shaft via the (n-1)th speed one-way clutch to the m-th speed one-way clutch, which are interposed therebetween, and a mechanical clutch. The n-th speed one-way clutch becomes idle. This results in the n-1st speed. Thereafter, the gears can be changed by sequentially engaging the hydraulic clutches in the same manner. In this case, there is no need to switch two or more hydraulic clutches at the same time. Note that in the above-mentioned speed change state, it is not possible to drive the first shaft from the second shaft, but when the reverse drive hydraulic clutch is engaged, the gear on the second shaft rotates integrally with the second shaft. This makes it possible to drive the first shaft from the second shaft. That is, engine braking can be used.

(f) Example (First example) 1 and 2 show a first embodiment of the present invention.

The output shaft 11 (
2nd axis) is arranged. The human power shaft 10 includes a first speed manual gear 12 and a fourth speed manual gear 1 in order from the right side in FIG.
4. A third speed manual gear $16 (mth speed gear) and a second speed manual gear 18 (nth speed gear) are arranged. These 1st speed manual gear 12, 4th gear manual gear 14, 3rd gear
The speed manual gear 16 and the second gear manual gear 18 are
l! It is rotatably supported relative to 11110. Further, the first speed manual gear 12 and the fourth speed manual gear 14 are connected to rotate together at all times. These first-speed manual gear 12 and fourth-speed manual gear 14 can be connected to or disconnected from the manual shaft 10 by a first hydraulic clutch C1. In addition, the second speed manual gear 18 and the third gear
The speed manual gear 16 is also connected to or disconnected from the manual shaft 10 by a second hydraulic clutch C2 (nth (=2) continuous hydraulic clutch) and a third hydraulic clutch C3 (nth (=3) continuous hydraulic clutch). It is possible.

On the output shaft 11, in order from the right side in FIG. A continuous output gear 26 (n-th speed gear) is arranged. The output gear 20 for the first speed is connected to the output shaft 11 and the first continuous one-way clutch O.
They are connected via WC. 4th speed river output gear 22
The reverse output gear 23 is rotatably supported with respect to the output shaft 11. The fourth output gear 22 can be connected to or disconnected from the output shaft 11 by means of the fourth dog clutch DC. The third output gear 24 is connected to the hollow shaft 25 via a third one-way clutch OWC3. The hollow shaft 25 is rotatably supported by the output shaft 11. Retraction output tooth 1t23 and hollow ■Iid+25
A dock clutch DC2 for forward/reverse switching is provided between the two. The forward/reverse switching dog clutch DC2 has a position connecting the reverse output gear 23 to the output 11i11111,
It is possible to switch between the position where the hollow shaft 25 and the output shaft 11 are connected. The second speed output gear 26 is connected to the third speed output gear 24 via a second one-way clutch OWC2. That is, the second continuous output gear 26 and the third speed output gear 24 are connected to the second continuous one-way clutch 0WC.
2 are connected in series. In addition, the second speed output gear 26 is connected to a fourth clutch C4 (hydraulic clutch for reverse drive).
It can be connected to or disconnected from the output shaft 11 by.

An idler shaft 34 provided parallel to the human power @ 10 and the output shaft 11 is provided with a backward idler gear 36 and a backward idler gear 38 that constantly rotate together with the idler shaft 34. The reverse idler gear 36 is always in mesh with the second speed manual gear 18 on the human power shaft 10, and is always in mesh with the reverse idler gear 38 and the reverse output gear 23 on the output shaft 11. In addition, for convenience of illustration, the reverse idler gear 38
Although the output gear 23 and the reverse output gear 23 are shown separated, they mesh with each other as described above. The first speed manual gear 12, the fourth speed manual gear 14, the third speed manual gear 16, and the second speed manual gear 18 are the first speed output gear 20, the fourth speed output gear 22, and the third speed output gear 22, respectively. Speed output gear 2
4 and the second speed output gear 26, thereby forming four gear pairs.

Next, the operation of this embodiment will be explained.

(1) Neutral By releasing the hydraulic clutches C1, 02, and c3, a neutral state is established in which no rotational force is transmitted from the human power Ikb io to the output I pongee 11. In this case, the dog clutches DC and DC2, and the fourth hydraulic clutch c4 may be in any state.

(2) First speed The first speed state is achieved by engaging only the first hydraulic clutch C1. That is, the rotational force from the human power shaft 10 is the first
It is transmitted to the output shaft 11 via the hydraulic clutch C1, the first speed manual gear 12, the first speed output gear 20, and the first continuous one-way clutch OWC. The gear ratio is determined by the ratio of the number of teeth between the first speed manual gear 12 and the first continuous output gear 20. In this case, the fourth continuous dog clutch D
C is set to the L side, that is, the non-4th speed side.

(3) Fasten the second hydraulic clutch C2 for the second speed and move the dog clutch DC2 for forward/reverse switching to F (travel side), that is, the hollow shaft 2
5 and the output shaft 11 are connected to each other, the state becomes the second speed state. In this case, it is acceptable to leave the first hydraulic clutch c1 engaged as the first continuous one-way clutch OWC will idle. By tightening the second hydraulic clutch C2, the rotational force of the human power shaft 1o is transferred to the second hydraulic clutch C2, the second speed manual gear 18, the second speed output gear 26, and the second one-way clutch ow.
c2, 3rd continuous one-way clutch 0WC3, hollow shaft 2
5 and the forward/reverse switching dog clutch DC2. The gear ratio is determined by the ratio of the number of teeth between the second speed manual gear 18 and the second continuous output gear 26.

Since the dog clutch DC2 for forward/reverse switching can be set to the forward side even in the first gear, all that is needed is to engage the second hydraulic clutch C2 when shifting from the first gear to the second gear. become.

(4) The third speed state is achieved by engaging the third hydraulic clutch C3 while leaving the third speed @reverse switching dog clutch DC2 in the forward position. In this case, the second hydraulic clutch C2 may remain engaged. The rotational force of the human power shaft 10 is determined by the third hydraulic clutch C3, the third gear gear tooth 16, the third gear output gear 24, and the third one-way clutch 0WC3.
, is transmitted to the output shaft 11 via the hollow shaft 25 and the forward/reverse switching dog clutch DC2. The gear ratio is determined by the ratio of the number of teeth between the third speed manual gear 16 and the third speed output gear 24. As mentioned above, the shift to the third gear is performed by engaging the third hydraulic clutch C3 while keeping the second hydraulic clutch C2 engaged, so in this case as well, the shift can be performed by switching only one hydraulic clutch. You will be killed. Note that the second continuous one-way clutch 0WC2 is in an idling state.

(5) Engage the 4th speed first hydraulic clutch C1 and move the 4th continuous dog clutch DC to the H (4th speed side) position (i.e., the 4th speed side)
By setting the position where the Hayakawa output tooth east 22 and the output shaft 11 are connected, the fourth speed state is achieved. In other words, the human power axis 10
The rotational force is transmitted to the output shaft 11 via the first hydraulic clutch C1, the fourth manual gear 14, the fourth output gear 22, and the fourth continuous dog clutch DC. The gear ratio is determined by the ratio of the number of teeth between the fourth gear 14 and the fourth continuous output gear 22.

In this case, the third hydraulic clutch C3 can remain engaged (the third continuous one-way clutch 0WC3
idling), only one hydraulic clutch change is required. In addition, in the case of shifting from 3rd speed to 4th speed, it is necessary to switch the 4th continuous dog clutch DC, but in reality, as mentioned above, shifting is performed simply by engaging the first hydraulic clutch C1. can be set. That is, in the second or third speed state, the first hydraulic clutch CI is released, and during this time, the fourth continuous dog clutch DC is
Switch to the speed side position (H position) in advance. Such an operation is possible because the traveling speed ranges of the first speed and the fourth speed are different, so there is no need to change gears between them. The switching of the fourth continuous dog clutch DC as described above is performed in a state where no rotational force is acting on the first speed output gear 20 and the fourth speed output gear 22, so a synchronization mechanism or the like is not required.

Note that in the fourth speed, since the one-way clutch is not interposed in the power transmission line, the human power shaft 10 can be driven from the output shaft 11 side, that is, the engine brake can be operated. Also in the second and third speeds, by engaging the fourth hydraulic clutch C4, it becomes possible to drive the human power shaft 10 side from the output shaft 11 side. That is, the fourth
When the hydraulic clutch C4 is engaged and the forward/reverse switching dog clutch DC2 is switched to the 1171 forward side, the second one-way clutch 0WC2 and the third one-way clutch 0WC3 become locked, and the second gear output tooth d
i 26 and the third speed output gear 24 are in a state of rotating together with the output shaft 11. Therefore, when the second hydraulic clutch C2 or the third hydraulic clutch C3 is engaged in this state, the second and third speeds are set, which can also be driven from the output shaft 11 side.

(6) Engage the second reverse hydraulic clutch C2 and move the forward/reverse switching dog clutch DC2 to the R side (reverse side) position (i.e.
By bringing the reverse output gear 23 and the output shaft 11 into a state in which they are integrally connected, a reverse state is achieved. That is, the rotational force from the human power shaft 10 is applied to the second hydraulic clutch C2, the second speed human power gear 18, the reverse idler gear 36, the idler support 34, the reverse idler gear 38, the reverse output gear 23, and the forward/reverse switching dog clutch. Output shaft 1 via DC2
1. Since the backward idler gear 36 and the reverse idler gear 38 are interposed in the power transmission path, the output shaft 11 rotates in the backward direction.

Note: The operating states of each element at each gear stage are summarized as shown in Fig. 2. The gear ratio shown in FIG. 2 is for the following number of teeth.

1st speed manual gear 12...14 1st speed output gear 20...41 4th speed manual gear 14...34 4th gear output gear jJL 22... 26 teeth for 3rd gear, 16...29 teeth for 3rd gear, 24...30 teeth for output for 2nd gear, 18...22 teeth for 2nd gear, output for 2nd gear 1' ! IIL 26...32 sheets,
In this embodiment, as can be seen from Fig. 2, 1st speed ← 3rd speed
It is also possible to change the speed by one step, such as from 2nd speed to 4th speed. This first embodiment is described in the above-mentioned Japanese Patent Application Laid-Open No. 59-208263.
Compared to the transmission shown in the publication, only two one-way clutches and one dog clutch have been added,
It has not become very large, and the price can be reduced by a small increase. Furthermore, as described above, a one-way clutch can be interposed in all gear shifts to facilitate shift control.

(Second Embodiment) Although the above-described first embodiment is a parallel shaft automatic transmission with four forward speeds, it may also be a parallel shaft automatic transmission with five forward speeds. In other words? ; As shown in Figure 3, the second speed output gear 50, third speed output gear 52, and fourth speed output gear 54 on the output shaft 11 side are connected in series by one-way clutches OW C2, OW C3, and 0WC4. 2nd speed output gear 5
0 can be connected or disconnected from the output shaft 11 by the reverse drive hydraulic clutch C5, and the fourth continuous output gear 54 can be connected to the output shaft 11 by the one-way clutch oWC4 and the forward/reverse switching dog clutch DC2. As in the first embodiment described above, 1←2←3←4←5 speeds can be performed, and since the speed change is performed by switching one clutch, the speed change control is facilitated.

As is clear from this, by providing the gear pair between the lowest gear and the highest gear with the structure of the present invention, the desired gear (the above two embodiments were 4th and 5th gear, respectively) can be set. It is possible to obtain a parallel shaft type automatic transmission (which may have six or more speeds).

(G) As described in detail, according to the present invention, gears from the m-th gear to the n-th gear 11 are connected in series by a one-way clutch, and these one-way clutches are connected by one hydraulic clutch. By increasing the required number of one-way clutches and one set of dog clutches, it becomes possible to perform all gear changes through one-way clutches, which simplifies gear change control.In other words, parallel shaft automatic gear shifting It becomes possible to simplify the speed change control without increasing the size of the machine or increasing the price, and it is also easy to increase the number of stages as necessary.

[Brief explanation of drawings]

1 is a diagram showing a first embodiment of a parallel shaft automatic transmission according to the present invention, FIG. 2 is a diagram showing a combination of operations of each element of the parallel shaft automatic transmission shown in FIG. 1, and FIG. The figure shows the second aspect of the present invention.
FIG. 1 is a diagram showing a parallel shaft automatic transmission according to an embodiment. 10...Human power axis (first axis), 11...Output axis (second axis)
shaft), 16... 3rd speed manual gear, 18... 2nd gear manual gear, 24... 3rd gear output gear, 26...
Second continuous output gear, C2...Second hydraulic clutch, C3
...Third hydraulic clutch, C4...Fourth clutch, 0
WC2... 2nd continuous one-way clutch, 0WC3.
...3rd speed river one-way clutch, DC2...dog clutch.

Claims (1)

[Scope of Claims] A plurality of pairs of gears meshing with each other are arranged on a first shaft and a second shaft arranged parallel to each other, and the connection state between each gear and the first shaft and the second shaft is controlled by a clutch. In a parallel shaft automatic transmission that enables automatic gear shifting,
The gears (n is a natural number) can be connected to or disconnected from the first shaft by hydraulic clutches for the n-th to m-th speeds, and the gears for the n-th to m-th speeds on the second shaft side are They are connected in series by one-way clutches for n-th to m-th speeds that are sequentially interposed between the gears, and the n-th speed gear on the second shaft is connected to the second shaft via a reverse drive hydraulic clutch. A parallel shaft automatic transmission characterized in that the m-th speed one-way clutch can be connected or disconnected from a second shaft via a mechanical clutch.