JPH01188741A - Speed change gear - Google Patents

Abstract

PURPOSE:To reduce the axial length of the captioned speed change gear by directly installing gears to an input rotary shaft, connecting an intermediate gear unit to these input shaft gears, and providing clutches on the intermediate gear unit between a first gear and a second gear coaxially provided with the first gear which are engaged with the input shaft gears. CONSTITUTION:As an input rotary shaft 2 is rotated, the turning force of an input-shaft gear 4 is transmitted to the first gear 14b of an inter-mediate gear unit 14 and the gear of a reverse gear unit, while the turning force of an input- shaft gear 5 is transmitted to the first gear 14d of the intermediate gear unit 14 and the first gear 16c of an intermediate gear unit 16. The turning force of the gear 14b of the intermediate gear unit 14 is further transmitted to an output shaft gear 8. In this case, when one of clutches 8', 14b', 14d', and 16c' is selectively engaged, the transmission of the turning force is carried out via the selected clutch to obtain a gear ratio which is determined by the diameter of the gear relating to the transmission of the turning force. When a clutch 20 is engaged or disengaged, a speed-changed turning force is outputted to a front-wheel or a rear-wheel driving force transmitting system.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a transmission, and in particular to a transmission that can shorten the length in the direction of the input rotational axis and further output output to two drive power transmission systems. Regarding. Such a transmission device is effectively used, for example, as a transmission device for an all-wheel drive automobile.

[Problem M to be solved by the prior art and the invention] As is well known, in an automobile, the driving rotational force from the output shaft of the engine is selectively changed at the appropriate time by the transmission to obtain the desired driving force. It is then transmitted to the drive wheels.

Conventionally, two-wheel parallel gear type transmissions have been widely used as such transmissions. This system generally has an input shaft and an output shaft extending in the direction of the engine output shaft, and a counter shaft arranged parallel to these two shafts, and uses multiple sets of gears with different gear ratios to connect these shafts. Combine selectively. Therefore, such a transmission is considerably long in the axial direction and is arranged in a manner that projects from the engine in the direction of its output shaft.

For this reason, the conventional transmission and engine as described above are quite long as a whole, which can be a constraint on automobile design, and is particularly an obstacle when trying to downsize automobiles.

Furthermore, in recent years, transversely mounted single engines have been used to make the drive power transmission system of passenger cars more compact.In this case, the transmission is placed in the width direction of the car body relative to the engine, so In particular, it is desirable to shorten the length due to the limitations.

Additionally, all-wheel drive (4WD) is a driving force transmission system that is advantageous for driving on rough roads, and has been increasingly applied to general vehicles in recent years. By the way, in this method, it is necessary to transmit rotational force from the engine to both the front wheel drive system and the rear wheel drive system via the transmission, so the driving force is branched and transmitted to the front wheel drive system or rear wheel drive system as necessary. A means is required to cut off the transmission of driving force to. As described above, 4WD has the disadvantage that the mechanism is more complicated and takes up a larger space than a front-wheel drive or rear-wheel drive drive power transmission system.

Therefore, in view of the problems of the prior art described above, the present invention makes it possible to sufficiently shorten the length in the axial direction, furthermore, it is possible to take out the output to two driving force transmission systems, and the driving force transmission system can be made more compact. The purpose is to provide a possible transmission device.

[Means for Solving the Problems] According to the present invention, in order to achieve the above objects, a gear is attached to the input rotating shaft via a clutch or directly, and an intermediate gear unit is attached to the input shaft gear. are connected to the intermediate gear unit, and the intermediate gear unit includes at least one first gear that directly or indirectly meshes with the input shaft gear, and at least one first gear that is axially disposed coaxially with the input shaft gear.
and a clutch between each of the second gears and each of the first gears, and the second gear of the intermediate gear unit is attached to the output rotating shaft via the clutch or directly. It is characterized in that it meshes directly or indirectly with a gear, and that the output rotating shaft is provided with means for branching the driving force to two driving force transmission systems. gearbox.

is provided. Here, indirect gear meshing refers to a case where rotational force is transmitted via an idle gear or the like.

The transmission of the present invention can be equipped with a gear unit for reverse rotation. Further, in the transmission of the present invention, a plurality of input shaft gears, output shaft gears, and/or intermediate gear units can be provided.

Furthermore, in the transmission of the present invention, the output rotating shaft has a shaft and a sleeve that is coaxial with the shaft and covered by a relatively rotatable ladder, and has a connecting means for connecting these shafts and the sleeve,
These constitute a driving force branching means, and two branched driving forces can be taken out from the sleeve and the shaft. In this case, the connection means between the shaft and the sleeve can be arranged at an axial position corresponding to at least one gear and/or at least one clutch of the intermediate gear unit.

Further, according to the present invention, there is provided an automobile equipped with the automatic transmission device as described above.

In the automobile of the present invention, the two driving force transmission systems can be a front wheel driving force transmission system and a rear wheel driving force transmission system.

[Example] Hereinafter, specific examples of the present invention will be described with reference to the drawings.

FIG. 1 is a schematic front view showing a transmission mechanism section of a first embodiment of a transmission device according to the present invention, and FIGS. 2, 3, and 4 are cross-sectional views taken along m sectional view and f
This embodiment, which is a sectional view taken along the line f-ff, is an example in which the transmission device is installed horizontally in an automobile, and has four forward speeds and one reverse speed.

In these figures, 2 is an input rotating shaft, and this shaft is a torque converter (not shown) connected to the engine output shaft.
is connected to the output shaft of the Two input shaft gears 4.5 are fixed to the input rotating shaft 2. In addition, 7 is an output rotation shaft arranged parallel to the input rotation shaft 2, and 6 is an output rotation sleeve rotatably placed on the shaft coaxially (however, in the M.M. book, the rotation (the sleeve is also included in the term "rotary shaft"), two output shaft gears 8.9 are attached to the sleeve 6, and the output shaft gear 8 is rotatably attached to the output rotation sleeve 6. 8' is a clutch for connecting these. Further, the output shaft gear 9 is fixed to the output rotation sleeve 6.

Input rotation axis 2. The output rotation sleeve 6 and the output rotation shaft 7 are rotatably supported by the housing IO. still,
In FIG. 1, the housing 10 is omitted from illustration.

The housing lO has two intermediate gear units 14.
16 is installed.

The intermediate gear unit 14 includes a rotating shaft 14a that is rotatably attached to the housing lO in parallel with the input rotating wheel 2 and the output rotating shaft 7, and a rotating shaft 14a that is rotatably attached to the rotating shaft and includes the input shaft gear 4 and the rotating shaft 14a. a first gear 14b meshing with the output shaft gear 8; a second gear 14c fixed to the rotating ring 14a and meshing with the output shaft gear 9; and a second gear 14c meshing with the output shaft gear 9;
4a, a first gear 14d that is rotatably attached to the input shaft gear 5 and meshes with the input shaft gear 5; a clutch 14b' that connects the rotating wheel 14a and the first gear 14b; and a clutch 14b' that connects the rotating wheel 14a and the first gear 14d. Clutch 1 that connects
It has 4d'.

The intermediate gear unit 16 includes a rotating shaft 16a that is rotatably attached to the housing 10 parallel to the input rotating shaft 2 and the output rotating shaft 7, and a #I2 that is fixed to the rotating shaft and meshes with the output shaft gear 9. Gear 16b, the rotating wheel le
a first gear 16C1 which is rotatably attached to a and meshes with the input shaft gear 5, the rotary wheel lea, and the first gear 16C1.
It has a clutch 16c' that connects the gear 16C.

A gear unit 18 for reverse rotation is also attached to the housing IO.

The gear unit) 1g includes a rotating shaft 18a rotatably attached to the housing lO parallel to the input rotating shaft 2 and the output rotating wheel 7, and a rotating shaft 18a rotatably attached to the rotating shaft and connected to the input shaft gear 4. a second gear 18b of the intermediate gear unit 16 fixed to the rotating shaft 18a;
The gear 16b, the gear 18c, and the rotating shaft 18
It has a clutch 18b' that connects the gear 18a and the gear 18b.

20 is a clutch that connects the output rotation shaft 6 and the output rotation sleeve 7, and is used to distribute driving force to the front wheel drive power transmission system and the rear wheel drive power transmission system.
As shown, the clutches include first gear 14d and clutch 14d' and first gear 18c and clutch ts.
It is arranged at an axial position corresponding to cB and is located within the housing lO.

The above clutches 8', 14b', 14d', 16c
For example, a hydraulically driven multi-plate clutch can be used as the clutches 18b' and 20, and a hydraulically driven dog clutch, which is advantageous for downsizing and cost reduction, can be used as the clutch 18b'.

A gear 22 is further fixed to the output rotation sleeve 6. The rotational force of the gear is connected via a differential (shown only in FIG. 2) 24 to drive rotary wheels (shown only in FIG. 2) 26 and 28 for both left and right driving wheels on the front side. A front wheel drive power transmission system includes these components.

Furthermore, a bevel gear (shown only in FIG. 2) 32 is fixed to the output rotating shaft 7, and the bevel gear is a rotating shaft (shown only in FIG. 2) 3 that transmits driving force to the rear wheels.
4 is meshed with a bevel gear (shown only in FIG. 2) 36.

A rear wheel drive power transmission system is configured including these.

Next, the operation of the apparatus of this embodiment will be explained.

When the input rotating wheel 2 rotates, the rotational force of the input shaft gear 4 is transmitted to the first gear 14b of the intermediate gear unit 14 and the gear 18b of the reverse rotation gear unit 18, and the rotational force of the input shaft gear 5 is transmitted to the intermediate gear unit 14. 14 first gear 14d and intermediate gear unit y) 16 first gear 16c. The rotational force of the first gear 14b of the intermediate gear unit 14 is further transmitted to the output shaft gear 8.

Here, the clutch 14b' of the intermediate gear unit 14 is turned to O.
When N, the rotational force of the first gear 14b is transmitted to the second gear 14c via the rotating shaft 14a, further transmitted to the output shaft gear 9 meshing with this gear, and then transmitted to the output rotating sleeve 6. be done.

Thus, the output rotating sleeve has a diameter of the input shaft gear 4, a diameter of the output shaft gear 9, and the first gear 14 of the intermediate gear unit 14.
The second gear 14c rotates at a speed ratio determined by the diameter of the second gear 14c of the intermediate gear unit. At this time, the clutches 8', 14d', 16c', and 18b' are OFF. The rotational force of the output rotation sleeve 6 is transmitted from a gear 22 to a rotation shaft 26 for driving the front wheels via a differential 24.
．． 28.

Further, when the clutch 14d' of the intermediate gear unit 14 is turned on, the rotational force of the first gear 14d is transferred to the rotation shaft 14a.
The signal is transmitted to the second gear 14c through the second gear 14c, and is further transmitted to the output shaft gear 9 meshing with the second gear 14c, and then to the output rotation sleeve 6. Thus, the output rotating sleeve has a gear ratio determined by the diameter of the input shaft gear 5, the diameter of the output shaft gear 9, the diameter of the first gear 14d of the intermediate gear unit 14, and the diameter of the second gear 14c of the intermediate gear unit. and rotate.

At this time, the clutches 8', 14b', 16c', 1
8b' is OFF. The rotational force of the output rotation sleeve 6 is transmitted from the gear 22 via the differential 24 to rotation shafts 26, 28 for driving the front wheels.

When the clutch 16c' of the intermediate gear unit 1B is turned on, the rotational force is transmitted in the same manner as when the clutch 14b' or 14d' of the intermediate gear unit 14 is turned on. At that time, the output rotating sleeve 6 is the diameter of the input shaft gear 5, the diameter of the output shaft gear 9, and the intermediate gear unit) 16.
The intermediate gear unit rotates at a speed ratio determined by the diameter of the first gear 18c and the diameter of the second gear 16b of the intermediate gear unit. At this time, the clutches 8', 14b', 14d', 18b'
is OFF.

On the other hand, when the clutch 18b' of the gear unit 18 for reverse rotation is turned on, the rotational force of the gear 18b is transmitted to the gear 18c via the rotating shaft 18a, and the rotational force of the gear 18b is further transmitted to the gear 18c of the intermediate gear unit 16 meshing with the gear. The signal is transmitted to the output shaft gear 9 via the second gear 16b, and then to the output rotation sleeve 6. that time.

The output rotating sleeve 6 is connected to the diameter of the input shaft gear 4 and the output shaft gear 9.
, the diameter of the gear 18b of the gear unit 18 for reverse rotation, and the diameter of the gear 18c of the gear unit 18. The rotational force of the output rotating sleeve 6 is transmitted through the gear 22.
is transmitted via the differential 24 to the rotation shafts 26, 28 for driving the front wheels. At this time, the clutches 8', 14b', 14d', and 16c' are 0FF-t'
be. In this case, the second gear 16 of the intermediate gear unit) 16
b acts as an idle gear.

Also, when the clutch 8' is turned on, the output shaft gear 8
The rotational force is immediately transmitted to the output rotating sleeve 6, and the output rotating sleeve rotates at a speed ratio determined by the diameter of the input shaft gear 4 and the diameter of the output shaft gear 8. At this time, the clutches 14b', 14d', 16c', and 1jllb' are at 0FF-1'. The rotational force of the output rotation sleeve 6 is transmitted from the gear 22 via the differential 24 to rotation shafts 26, 28 for driving the front wheels. In this case, the first gear 14b of the intermediate gear unit 14 serves as an idle gear.

As mentioned above, clutches 8', 14b', 14d', 16
c', 18b'7) When one of 17) is selectively engaged, rotational force is transmitted via the selected clutch, and a gear ratio determined by the diameter of the gear related to transmission of rotational force is obtained. be able to.

Clutches 8', 14b', 14d' in this embodiment
, 16c', and tab' and an example of the relationship between the gear ratio and the gear ratio are shown in Table 1 below.

Table 1 When the clutch 20 is turned off, the rotational force shifted as described above is output only to the front wheel drive power transmission system.

On the other hand, when the clutch 20 is turned on, the rotational force of the output rotation sleeve 6 is transmitted to the output rotation shaft 7, and is also output to the rear wheel drive force transmission system.

In this way, in this embodiment, it is possible to switch between front wheel drive and 4WD as necessary.

According to this embodiment as described above, the axial length can be sufficiently shortened as shown in FIGS. 2 to 4. Furthermore, since the output shaft gears 8 and 9 attached to the output rotating sleeve 6 are arranged unevenly within the housing O,
The clutch 20 is housed within the housing to achieve compactness.

FIG. 5 is a schematic front view showing the transmission mechanism section of the second embodiment of the transmission device according to the present invention, and FIGS. ■Cross-sectional view and ■
-■ Cross-sectional view 0 This embodiment is an example in which the transmission is installed horizontally in an automobile, and is a transmission with five forward speeds and one reverse speed. In these figures, members similar to those in FIGS. 1 to 4 are given the same reference numerals (excluding the constituent members of the intermediate gear unit and the reverse rotation gear unit).

In this embodiment, the input rotating shaft 2 has input shaft gears 1 and 3.
, 4.5 are installed. The input shaft gear 1 is fixed, and the input shaft gear 3 is attached via a clutch 3'.

The intermediate gear unit 14 has first gears 14b, 14d, and a second gear 14c, and the gears 14b and 14d are attached to the rotating shaft 14a via clutches 14b' and 14d', respectively, and the gear 14C is attached to the rotating shaft 14a. 14a.

The intermediate gear unit 16 has first gears tsb, tsd, and a second gear 16c, and the gears 16b and 16d are attached to the rotating shaft lea via clutches 16b' and led', respectively, and the gear 16C is attached to the rotating shaft lea. 16a.

The gear unit 18 for reverse rotation has gears 18b and 18C, and the gear 18b connects to the rotating shaft 18a via a clutch 18b'.
The gear 18c is fixed to the rotating shaft 18a.

21 is a differential, and the output shaft gear 8 is attached as its ring gear. Output rotation sleeves 6a and 6b are connected to the two side gears of the differential, respectively, and a visco unit 23 is interposed between the sleeves 6b and the output rotation shaft 7. The driving force branching means includes these components.

The above clutches 3', 14b', 14d', 18b', 1
As 6d' and 18b', for example, a hydraulically driven dog clutch, which is advantageous for downsizing and cost reduction, can be used.

In this embodiment, the gear meshing is as follows.

1φ...Fist 14b, 16b 30φ・Fist・16c 4...16d 51 fist...14d 14b...18b 8・11+1...14c, 16c, 18c Clutches 3', 14b' in this embodiment , 14d', 16b', 1
An example of the relationship between the selection of 6d' and 18b' and the gear ratio is shown in Table 2 below.

According to this embodiment as shown in Table 2 and above, the axial length can be sufficiently shortened as shown in FIGS. 6 to 8. Furthermore, since the output shaft gear 8 is arranged unevenly within the housing 10, the differential 21 constituting the driving force branching means is accommodated within the housing, thereby achieving compactness.

[Effects of the Invention] As explained in detail above, according to the present invention, the axial length of the transmission can be sufficiently shortened, and based on this, the degree of freedom in designing the driving force transmission system can be increased. It can be improved dramatically.

Further, according to the present invention, output can be taken out to two driving force transmission systems, and the driving force transmission system can be made more compact.

[Brief explanation of the drawing]

FIG. 1 is a schematic front view showing a transmission according to the present invention, and FIGS. 2, 3, and 4 are a sectional view taken along the line 1, 2, and 4, a sectional view taken along the line mm, and a sectional view taken along the line 2, respectively. be. FIG. 5 is a schematic front view showing the transmission according to the present invention, and FIGS. 6, 7, and 8 are a sectional view along the line 1, 2, and 8, respectively. be. 1. 3, 4, 5: Input shaft gear, 2 two-man power rotation shaft. 6.6a, 6b: Output rotating sleeve. 7: Output rotating shaft, 8, 9: Output shaft gear. 10: Housing, 14.16: Intermediate gear unit, 18: Reverse rotation gear unit, 20: Clutch 1 21.24: Differential. 22: Gya, 23: Visco unit. 26, 28: Drive shaft, 32.36: Bevel gear, 34: Rotating shaft. Figure 2 Figure 5 Figure 6

Claims (1)

[Claims] (1) A gear is attached to the input rotating shaft via a clutch or directly, and an intermediate gear unit is connected to the input shaft gear, and the intermediate gear unit is connected to the input shaft gear. At least one first gear that meshes with the gear directly or indirectly, at least one second gear coaxially disposed with the gear, and between each of the second gears and each of the first gears. The second gear of the intermediate gear unit meshes directly or indirectly with a gear attached to the output rotating shaft via a clutch or directly, and the output rotating shaft has two clutches. characterized by being provided with means for branching the driving force into two driving force transmission systems,
gearbox. (2) Equipped with a gear unit for reverse rotation,
The transmission according to claim 1. (3) The transmission according to claim 1 or 2, comprising a plurality of input shaft gears. (4) The transmission according to any one of claims 1 to 3, comprising a plurality of output shaft gears. (5) The transmission according to any one of claims 1 to 4, wherein a plurality of intermediate gear units are provided. (6) The output rotating shaft has a shaft and a sleeve coaxially placed over the shaft so as to be relatively rotatable, and has a connecting means for connecting these shafts and the sleeve, and these constitute a driving force branching means. The transmission according to any one of claims 1 to 5, wherein two branched driving forces are extracted from the sleeve and the shaft. (7) The transmission according to claim 6, wherein the connection means between the shaft and the sleeve is arranged at an axial position corresponding to at least one gear and/or at least one clutch of the intermediate gear unit. (8) An automobile equipped with the transmission according to any one of claims 1 to 7. (9) The automobile according to claim 8, wherein the two drive power transmission systems are a front wheel drive power transmission system and a rear wheel drive power transmission system.