JPH0821492A - Power transmission device for vehicle - Google Patents

Abstract

PURPOSE:To reduce the dimension of a power transmission device for vehicle which supplies and receives a torque between wheels by a pair of hydraulic clutches which can transmit the torque each other. CONSTITUTION:The ring gear 4 of a differential gear device D is connected with an engine E, and a sun gear 5 and a planetary carrier 8 are connected with the left and right output shafts 9L and 9R, respectively. On a carrier member 11 which is fitted in a rotatable manner with the left output shaft 9L, the first and the second pinions 13 and 14 which are integrally formed and have the respective pitch diameters are supported, and the first pinion 13 is connected with the right output shaft 9R, and the second pinion 14 is connected with the left output shaft 9L. If, in the rightward turn, a hydraulic clutch Cd is engaged, the carrier member 11 is decelerated, and the left front wheel WFL increases speed, and the torque is transmitted to the left front wheel WFL. In the leftward turn, if a hydraulic clutch Ca is engaged, the carrier member 11 increases speed, and the right front wheel WFR is accelerated, and the torque is transmitted to the right front wheel WFR.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device for a vehicle which supplies torque between left and right wheels or front and rear wheels by providing torque transmission means capable of mutually transmitting torque between two rotary shafts. Regarding

[0002]

2. Description of the Related Art A differential device provided in a power transmission system of a vehicle is constructed so as to absorb a rotational speed difference generated between left and right wheels when the vehicle turns, and transmit engine torque evenly to the left and right wheels. . However, it is desirable to transmit more torque to the outer turning wheel to improve the turning performance when the vehicle is running at low speeds, and to transmit more torque to the inner turning wheel to improve the running stability performance when running at high speed.

Therefore, a vehicle power transmission device that actively controls a differential device based on a rotation angle of a steering wheel or a vehicle speed and transmits a torque suitable for a driving state at that time to the left and right wheels is disclosed in Japanese Patent Laid-Open No. Hei 5 (1999) -53. It is known from JP-A-131855.

[0004]

By the way, in the above-mentioned conventional power transmission device for a vehicle, since the rotary shafts are arranged radially outside the pair of hydraulic clutches, the size thereof becomes large and the device is mounted on the vehicle. There is a problem that becomes difficult.

The present invention has been made in view of the above circumstances, and the rotary shaft of the vehicle power transmission device is eliminated.
The purpose is to reduce the size.

[0006]

In order to achieve the above object, the invention described in claim 1 is a power transmission for a vehicle, which is provided with a torque transmission means capable of mutually transmitting torque between two rotating shafts. In the device, the torque transmission means includes a carrier member rotatably supported around one rotation shaft,
A first gear and a second gear integrally formed with different pitch radii and rotatably supported by the carrier member.
A gear, a connecting means for connecting the first gear and the second gear to both rotary shafts, a carrier member speed increasing means for speeding up the carrier member, and a carrier member speed reducing means for speeding down the carrier member. It is characterized by being done.

In addition to the structure of claim 1, the invention according to claim 2 is characterized in that the carrier member speed increasing means has three elements of a sun gear, a ring gear and a planetary carrier, and the first element is the above-mentioned. A planetary gear unit connected to one of the rotating shafts, the second element being connected to the carrier member;
And a speed-up clutch that connects the third element of the planetary gear device to a fixed member.

The invention described in claim 3 is characterized in that, in addition to the structure of claim 1, the carrier member speed reducing means is composed of a speed reducing clutch for connecting the carrier member to a fixed member. .

According to a fourth aspect of the present invention, in addition to the structure of the first aspect, the carrier member deceleration means has a first structure.
It is characterized by comprising a deceleration clutch that connects a restraining ring gear that meshes with the gear or the second gear to the fixed member.

[0010]

Embodiments of the present invention will be described below with reference to the drawings.

1 to 3 show a first embodiment of the present invention. FIG. 1 is a skeleton diagram showing a power transmission system of a front engine / front drive vehicle, and FIG. FIG. 3 is an explanatory view of the action when turning left.

As shown in FIG. 1, the vehicle is mounted horizontally at the front of the vehicle.
Transmission M is connected to the right end of the mounted engine E
The engine E and transmission
Torque transmission means T is arranged at the rear of M. Torque transmission
A left axle A extending left and right from the left and right ends of the means T_LOver
And right axle A_RTo the left front wheel W respectively_FLAnd the right front wheel W _FR
Are connected.

The torque transmitting means T comprises a differential device D to which a driving force is transmitted from an external gear 3 which meshes with an input gear 2 provided on an input shaft 1 extending from a transmission M.
The differential device D comprises a double pinion type planetary gear mechanism, and a ring gear 4 formed integrally with the external gear 3.
A planetary gear supporting the sun gear 5 coaxially arranged inside the ring gear 4, the outer planetary gear 6 meshing with the ring gear 4 and the inner planetary gear 7 meshing with the sun gear 5 in a mutually meshing state. It is composed of a carrier 8. The differential device D
The ring gear 4 functions as an input element, the sun gear 5 that functions as one output element is connected to the left front wheel W _FL via the left output shaft 9 _L, and the planetary carrier 8 that functions as the other output element. Is the right output shaft 9
It is connected to the right front wheel W _FR via _R. The left output shaft 9 _L and the right output shaft 9 _R form the rotating shaft in the present invention.

A plurality of pinion shafts 12 are formed at the right end of a carrier member 11 rotatably supported on the outer periphery of the left output shaft 9 _L , and the first pinion 13 and the second pinion 1 are formed.
The four integrally formed members are rotatably supported by the respective pinion shafts 12. The first sun gear 15, which is rotatably supported on the outer periphery of the left output shaft 9 _L and meshes with the first pinion 13, is connected to the planetary carrier 8 of the differential device D. The second sun gear 16 fixed to the outer circumference of the left output shaft 9 _L meshes with the second pinion 14.

The number of teeth of the first sun gear 15 is Za, the number of teeth of the second sun gear 16 is Zb, and the number of teeth of the first sun gear 15 is larger than that of the second sun gear 16 (Za
> Zb) is set. The number of teeth of the first pinion 13 is Zc, the number of teeth of the second pinion 14 is Zd, and the number of teeth of the first pinion 13 is smaller than the number of teeth of the second pinion 14 (Zc <Zd). Is set. In this case,
First sun gear 15, second sun gear 16, first pinion 1
The modules of 3 and the second pinion 14 are set equal.

The second sun gear 16 constitutes a connecting means for connecting the second pinion 14 to the left output shaft 9 _L , and the first sun gear 15 and the planetary carrier 8 connect the first pinion 13 to the right output shaft 9 _R. Constitutes a means.

A deceleration hydraulic clutch Cd is arranged between the carrier member 11 and the casing 17 as a fixed member. The deceleration hydraulic clutch Cd decelerates the rotation speed of the carrier member 11 by its engagement, and constitutes the carrier member deceleration means DM of the present invention.

A double pinion type planetary gear device P provided at the left end of the carrier member 11 includes a ring gear 18 fixed to the left output shaft 9 _L , a sun gear 19 fixed to the carrier member 11, and the ring gear 18. The outer planetary gear 20 meshes with the inner planetary gear 21 that meshes with the sun gear 19, and the planetary carrier 22 supports the inner planetary gear 21 so as to mesh with each other. The planetary carrier 22 is a hydraulic clutch Ca for acceleration.
It can be connected to the casing 17 via. The planetary gear device P and the speed increasing hydraulic clutch Ca increase the rotational speed of the carrier member 11 by engagement of the speed increasing hydraulic clutch Ca, and constitute the carrier member speed increasing means AM of the present invention.

Since the decelerating hydraulic clutch Cd and the speed increasing hydraulic clutch Ca are disposed between the casing 17 and the casing 17, an oil passage for supplying / discharging the hydraulic oil to / from the hydraulic clutches Ca and Cd is casing. 17 can be formed, which can simplify the structure.

The electronic control unit 23, to which the vehicle speed V and the steering angle θ are input, controls the decelerating hydraulic clutch Cd and the speed increasing hydraulic clutch Ca via the hydraulic circuit 24.

Next, the operation of the first embodiment of the present invention having the above construction will be described.

When the vehicle is traveling straight ahead, both the deceleration hydraulic clutch Cd and the speed increasing hydraulic clutch Ca are disengaged. Thereby, restraint of the carrier member 11 and the planetary gear unit P of the planetary carrier 22 is released, the left axle 9 _L, the right axle 9 _R, the planetary carrier 8 of the differential D, the carrier member 11 and the planetary gear unit P planetary The carriers 22 all rotate together. At this time,
As indicated by the hatched arrows in FIG. 1, the torque of the engine E is evenly transmitted from the differential device D to the left and right front wheels W _FL and W _FR .

Now, when the vehicle turns right, as shown in FIG.
Via electronic control unit 23 and hydraulic circuit 24
The hydraulic clutch Cd for speed is engaged and the carrier member 11 is closed.
To the housing 17. At this time, the left front wheel W_FLTogether with
Left output shaft 9_LAnd the right front wheel W _FRRight output shaft 9 integrated with
_R(That is, the planetary carrier 8 of the differential device D)
Second sun gear 16 (number of teeth Zb), second pinion 14 (teeth
Number Zd), first pinion 13 (number of teeth Zc) and first sun
Since it is connected via gear 15 (number of teeth Za),
Front wheel W_FLRight front wheel W_FRFor (Za / Zc) × (Zd
/ Zb). That is, the left front wheel W_FLRotation of
Number N_LAnd the right front wheel W_FRNumber of revolutions N_RBetween

[0024]

[Equation 1]

The following relationship is established.

As described above, the rotation speed N of the left front wheel W _FL
When _L is increased relative to the rotational rate N _R of the right front wheel W _FR, as indicated by the hatched arrow in FIG. 2, turning outer part of the torque of an inner wheel right front wheel W _FR Left front wheel W _FL
Can be transmitted to.

Instead of stopping the carrier member 11 with the deceleration hydraulic clutch Cd, the engaging force of the deceleration hydraulic clutch Cd is appropriately adjusted to decelerate the rotation speed of the carrier member 11, and the left side is decelerated according to the deceleration. Front wheel W _FL speed N
Increasing the _L relative to the rotational speed N _R of the right front wheel W _FR Hayashi, it is possible to transmit any torque to the left front wheel W _FL as a turning-outer right front wheel W _FR as a turning-inner.

On the other hand, when the vehicle is turning to the left, as shown in FIG. 3, the speed increasing hydraulic clutch Ca is engaged via the electronic control unit 23 and the hydraulic circuit 24, and the planetary carrier 22 of the planetary gear unit P is accommodated in the casing 17. Bind to. As a result, the rotation speed of the left output shaft 9 _L (that is, the ring gear 18
The number of rotations of the carrier member 11 (that is, the number of rotations of the sun gear 19 (number of teeth Zf)) with respect to (the number of rotations of the number of teeth Ze) is
The speed is increased at the Ze / Zf ratio, and the rotational speed N _R of the right front wheel W _FR is increased.
Is increased by the following relationship with the rotational speed N _L of the left front wheel W _FL .

[0029]

[Equation 2]

As is clear from comparison between the equations (1) and (2), Ze / Zf, which is the ratio of the number of teeth Ze of the ring gear 18 to the number of teeth Zf of the sun gear 19 of the planetary gear device P.
By setting the value to be slightly over 2.0, the right front wheel W _{FR is changed} to the left front wheel W _FR.
The speed increase rate to _FL and the speed increase rate from left front wheel W _FL to right front wheel W _FR can be made substantially equal.

As described above, the rotation speed N of the right front wheel W _FR.
When _R is increasing relative to the rotational rate N _L of the left front wheel W _FL, as indicated by the hatched arrow in FIG. 3, the turning part of the torque of a turning inner front left wheel W _FL outer Right front wheel W _FR
Can be transmitted to. Also in this case, if the rotational speed of the carrier member 11 is increased by appropriately adjusting the engaging force of the speed increasing hydraulic clutch Ca, the rotational speed N _R of the right front wheel W _FR is changed according to the speed increase. Speed is increased with respect to the rotational speed N _{L of FL} , and the left front wheel W _FL, which is the inner turning wheel, to the right front wheel W _FR, which is the outer turning wheel.
Any torque can be transmitted to.

By setting the speed increasing rate in the range of 1.05 to 1.20 and adjusting the engaging forces of the decelerating hydraulic clutch Cd and the speed increasing hydraulic clutch Ca, the left and right sides of the vehicle under normal traveling conditions are controlled. It is possible to freely distribute the torque between the front wheels W _FL and W _FR . In other words, when the vehicle is running at low speeds, the torque that is transmitted to the turning outer wheels is greater than that of the turning inner wheels to improve turning performance, and when the vehicle is running at high speeds, the torque that is transmitted to the turning outer wheels is reduced compared to when the vehicle is running at low speeds. It is possible to improve stability performance.

Thus, according to this embodiment, it is not necessary to dispose the rotary shafts outside the deceleration hydraulic clutch Cd and the speed-up hydraulic clutch Ca, so that the radial dimension of the vehicle power transmission device is reduced. It can be made compact.

Next, a second embodiment of the present invention will be described with reference to FIG.

In the second embodiment, the carrier member speed reducing means DM
2 and the structure of the carrier member speed increasing means AM are different from those of the first embodiment, and other structures are the same as those of the first embodiment.

That is, the carrier member speed reducing means DM including the speed reducing hydraulic clutch Cd connects the restraining ring gear 25 meshing with the first pinion 13 to the casing 17. When the rotation of the restraining ring gear 25 is stopped or decelerated by the deceleration hydraulic clutch Cd during right turn,
When the first pinion 13 and the second pinion 14 supported by the carrier member 11 perform a planetary motion, the left front wheel W
Rotational speed N _L of _FL is increased relative to the rotational rate N _R of the right front wheel W _FR, part of the torque of an inner wheel right front wheel W _FR is transmitted to the left front wheel W _FL is the outer turning wheel. Instead of engaging the restraining ring gear 25 with the first pinion 13,
It may be meshed with the pinion 14.

On the other hand, the carrier member speed increasing means AM comprises a planetary gear unit P and a speed increasing hydraulic clutch Ca. The planetary gear unit P includes a ring gear 18, a sun gear 19,
The planetary carrier 22 and the planetary gear 26 are provided. The ring gear 18 is formed integrally with the carrier member 11. The sun gear 19 can be connected to the casing 17 by the hydraulic clutch Ca for speed up.
Is coupled to the left output shaft 9 _L.

When the rotation of the sun gear 19 is stopped or restricted by the speed increasing hydraulic clutch Ca during the left turn, the rotation of the left output shaft 9 _L is increased through the planetary carrier 22, the planetary gear 26 and the ring gear 18. It is transmitted to the carrier member 11. This rotational speed N _R of the right front wheel W _FR is increased relative to the rotational rate N _L of the left front wheel W _FL, the right front wheel W _FR part of the torque of the left front wheel W _FL as a turning-inner is the outer turning wheel Be transmitted to.

Thus, according to the second embodiment as well, the rotary shafts can be eliminated from the outside of the deceleration hydraulic clutch Cd and the speed-up hydraulic clutch Ca, and the vehicle power transmission device can be made compact.

Although the embodiment of the present invention has been described in detail above, the present invention is not limited to the above embodiment, and various design changes can be made.

For example, the vehicle power transmission device of the present invention is not limited to transmitting torque between the left and right drive wheels, but can also be used for transmitting torque between the front and rear drive wheels in a four-wheel drive vehicle. It can also be used as a power transmission device between non-driving wheels. Further, the deceleration hydraulic clutch Cd and the speed-up hydraulic clutch Ca can be replaced with an electromagnetic clutch or a fluid coupling.

[0042]

As described above, according to the first aspect of the present invention, the torque is transmitted from one rotary shaft to the other rotary shaft by accelerating the carrier member by the carrier member accelerating means. Since the torque can be transmitted from the other rotary shaft to the one rotary shaft by increasing the speed of the carrier member by the carrier member decelerating means, it is possible to improve the turning performance and running stability performance of the vehicle. . Further, since the carrier member rotatably supported around one of the rotary shafts is only accelerated and decelerated, the rotary shaft arranged outside the conventional clutch can be eliminated and the power transmission device can be downsized.

According to the invention described in claim 2,
Since the carrier member can be speeded up with a simple structure, and the speed increasing clutch is arranged between the fixed member,
When a hydraulic clutch is used, it is possible to easily form an oil passage for supplying and discharging hydraulic oil.

According to the third or fourth aspect of the present invention, the carrier member can be decelerated with a simple structure, and the deceleration clutch is arranged between the fixed member and the hydraulic clutch. When adopted, an oil passage for supplying and discharging hydraulic oil can be easily formed.

[Brief description of drawings]

FIG. 1 is a skeleton diagram showing the power transmission system of a front engine / front drive vehicle.

FIG. 2 is an explanatory view of the action when turning right.

FIG. 3 is an explanatory view of the action when turning left.

FIG. 4 is a diagram corresponding to FIG. 1 according to the second embodiment.

[Explanation of symbols]

8 planetary carrier (coupling means) 9 _L left output shaft (rotating shaft) 9 _R right output shaft (rotating shaft) 11 carrier member 13 first pinion (first gear) 14 second pinion (second gear) 15 first sun gear (Connecting member) 16 Second sun gear (connecting member) 17 Casing (fixing member) 18 Ring gear 19 Sun gear 22 Planetary carrier 25 Restraint ring gear AM Carrier member speed increasing means DM Carrier member speed reducing means Ca Speed increasing hydraulic clutch (speed increasing) Clutch) Cd deceleration hydraulic clutch (deceleration clutch) P planetary gear device T torque transmission means

Claims (4)

[Claims] 1. A vehicle power transmission device comprising torque transmitting means (T) capable of mutually transmitting torque between two rotating shafts (9 _L , 9 _R ), wherein the torque transmitting means (T) is A carrier member (11) rotatably supported around one rotation shaft (9 _L ) is integrally formed with different pitch radii, and is rotatably supported by the carrier member (11). A first gear (13) and a second gear (14), and a connecting means (8, 15,) for connecting the first gear (13) and the second gear (14) to both rotary shafts (9 _L , 9 _R ). 1
6), carrier member accelerating means (AM) for accelerating the carrier member (11), and carrier member decelerating means (DM) for decelerating the carrier member (11). A power transmission device for a vehicle. 2. The carrier member accelerating means (AM) has three elements of a sun gear (19), a ring gear (18) and a planetary carrier (22), the first element being the one rotating shaft (9). _L ) and a second element connected to the carrier member (11) with a planetary gear set (P) and a third member of the planetary gear set (P) with a fixing member (1).
The power transmission device for a vehicle according to claim 1, wherein the power transmission device includes a speed increasing clutch (Ca) connected to 7). 3. The carrier member deceleration means (DM) comprises:
2. The vehicle power transmission device according to claim 1, wherein the power transmission device for a vehicle comprises a reduction clutch (Cd) for connecting the carrier member (11) to the fixing member (17). 4. The carrier member deceleration means (DM) comprises:
A reduction clutch (Cd) for connecting a restraining ring gear (25) meshing with the first gear (13) or the second gear (14) to a fixed member (17). The vehicle power transmission device described.