JP7249734B2 - transmission - Google Patents

Description

The present invention relates to transmissions.

Conventionally, as disclosed in Patent Document 1 below, in a transmission, an input shaft and an output shaft are rotatably connected to each other. to the output shaft. In the transmission disclosed in Patent Document 1 below, an output shaft is supported by two bearings fixed to a transmission case. The input shaft has one end supported by the output shaft and the other end supported by a bearing fixed to the transmission case. Thus, in the conventional transmission, the output shaft is supported by two bearings in the transmission case, and the input shaft is supported by the output shaft and the transmission case.

Japanese Patent Application Laid-Open No. 2004-301206

However, when the input shaft and the output shaft are pivotally supported using three bearings fixed to the transmission case, as in the transmission disclosed in Patent Document 1, various design restrictions are imposed. There is a problem that arises. Specifically, in the transmission and the like of Patent Document 1, it is necessary to use a large amount of space in the transmission case in order to fix the bearings to the transmission case, and the design freedom in the transmission case is increased. is restricted, and the transmission case is lengthened, which restricts the degree of freedom in designing a vehicle or the like in which the transmission is mounted. Therefore, there is a demand to reduce as much as possible the number of bearings that are used to axially support the input shaft and the output shaft to the transmission case and are fixed to the transmission case.

SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a transmission in which an input shaft and an output shaft can be supported on a transmission case while increasing the degree of design freedom.

The transmission of the present invention, which is provided to solve the above-described problems, includes a first shaft and a second shaft capable of transmitting rotational force from one side to the other in a transmission case, two or more first bearings that are not fixed to a transmission case and are capable of mutually supporting the first shaft and the second shaft; and a first bearing that is fixed to the transmission case and supports the first shaft. and a third bearing that is fixed to the transmission case and supports the second shaft, wherein one end of the second shaft is provided with a recess so that the at least a portion of which is inserted into the recess, the third shaft and at least a portion of the first bearing overlap , and the third shaft and at least a portion of the first shaft overlap each other; It is characterized by overlapping in the direction .

The transmission of the present invention integrates the first shaft and the second shaft through two or more first bearings. By integrating the first shaft and the second shaft through two or more first bearings, the first shaft and the second shaft are relatively bent while allowing differential rotation, so that each shaft becomes Displacement in the radial direction of the shaft can be suppressed. Further, in the integrated first shaft and second shaft, the first shaft is supported by the second bearing fixed to the transmission case, and the second shaft is supported by the third bearing fixed to the transmission case. By supporting, the integrated first shaft and second shaft are supported on the transmission case while allowing differential rotation of the respective shafts and suppressing displacement in the radial direction of the shafts. can be done. By supporting the integrated first shaft and second shaft on the transmission case only with the second bearing and the third bearing, the number of bearings fixed to the transmission case can be minimized. Restrictions on the degree of freedom in designing the inside of the transmission case are suppressed, and restrictions on the degree of freedom in designing the vehicle or the like in which the transmission is mounted due to the lengthening of the transmission case are suppressed.

In the above-described transmission of the present invention, a recess is provided at one axial end of the first shaft, at least a portion of the second shaft is inserted into the recess, and all of the first bearings are provided with the recess. and the outer peripheral surface of the second shaft.

With such a configuration, the first shaft and the second shaft can be mutually supported within the recess, so the size of the configuration for supporting the first shaft and the second shaft can be minimized. Therefore, restrictions on the degree of freedom in designing the inside of the transmission case are further suppressed, and restrictions on the degree of freedom in designing the vehicle or the like in which the transmission is mounted due to the lengthening of the transmission case are suppressed.

In the transmission of the present invention described above, it is desirable that at least one of the first bearing, the second bearing and the third bearing is a bearing.

According to such a configuration, even when the rotation speed of the first shaft or the second shaft is high, the shaft can be easily rotatably supported, and the first shaft or the second shaft can be moved in the axial direction. can be suppressed.

According to the present invention, it is possible to provide a transmission in which the input shaft and the output shaft can be supported on the transmission case while increasing the degree of design freedom.

1 is a cross-sectional view of a transmission according to an embodiment of the invention; FIG. FIG. 4 is a diagram showing the correspondence between operating states of clutches and brakes and gear positions of a transmission according to one embodiment of the present invention;

Hereinafter, a transmission 10 according to one embodiment of the present invention will be described in detail with reference to the drawings. Hereinafter, the configuration of the transmission 10 will be briefly described first, and then the configuration of the second output shaft 21 and the third output shaft 22 that are integrated and mutually supported, which is a unique configuration of the transmission 10, will be described in detail. do.

<<Regarding the configuration of the transmission 10>>
The transmission 10 is a so-called FR type transmission. As shown in FIG. 1, the transmission 10 includes a torque converter 12, an input shaft 14 connected to the engine via the torque converter 12, a clutch C, a brake B, a first planetary gear mechanism 16, a second planetary gear mechanism. 18 , a first output shaft 20 , a second output shaft 21 , a third output shaft 22 , etc. are provided inside the transmission case 24 . A valve body 26, an oil pan 28, and the like are provided below the first planetary gear mechanism 16 and the second planetary gear mechanism 18, respectively.

The first planetary gear mechanism 16 can input the power transmitted from the engine to the input shaft 14 via the torque converter 12 via transmission control elements such as the clutches C1 to C3, the brakes B1 and B2, and the one-way clutch F. It is said that The first planetary gear mechanism 16 includes a front planetary sun gear 16a, a rear planetary sun gear 16b, a planetary short pinion 16c, a planetary long pinion 16d, a planetary carrier 16e, a planetary ring gear 16f, and the like.

The first planetary gear mechanism 16 has three power transmission paths as input paths. Specifically, the first planetary gear mechanism 16 has, as an input path, a first path from the input shaft 14 via the clutch C1 to the front planetary sun gear 16a. In addition, the first planetary gear mechanism 16 has a second path that is transmitted to the rear planetary sun gear 16b via the clutch C2, and a third path that is transmitted to the first output shaft 20 and the planetary carrier 16e via the clutch C3. has a route of In addition, the first planetary gear mechanism 16 has a path output from the planetary ring gear 16f as an output path. Power output from the planetary ring gear 16 f can be output to the third output shaft 22 via the second output shaft 21 .

Further, shift control elements such as clutches C1 to C3, brakes B1 and B2, and one-way clutch F operate as shown in FIG. ). Thereafter, when the shift control element operates as shown in FIG. 2 in each shift stage, the first planetary gear mechanism 16 operates as described in detail below.

When the gear stage is 1st gear and the shift lever is in the D range or 2nd range (no engine braking), the clutch C2 and the one-way clutch F operate to shift the gear in the forward direction (for example, right) at a predetermined gear ratio. direction) can be output. Specifically, in this state, since the clutch C2 is operating, the rotational force of the input shaft 14 is directly transmitted to the rear planetary sun gear 16b, and is transmitted to the planetary short pinion 16c in the opposite direction (for example, leftward direction). to transmit the rotational force to the On the other hand, the planetary long pinion 16d, which meshes with the planetary short pinion 16c, tries to rotate the planetary carrier 16e in the reverse direction by receiving a rotational force in the forward direction. However, since the rotation is blocked by the action of the one-way clutch F, the planetary ring gear 16f receives rotational force in the forward direction and outputs rotational force in the forward direction.

When the gear stage is 1st gear and the shift lever is in the L range (with engine braking), rotation is performed in the same manner as when the gear stage is 1st gear and the shift lever is in the D range or 2nd range. introduce. However, when the shift lever is in the L range, the brake B2 exerts an action to prevent the planetary carrier 16e from rotating in the forward direction during engine braking. Different from being a range. That is, when the gear stage is 1st gear and the shift lever is driven in the D range or 2nd range, the reverse rotation of the planetary carrier 16e is locked by the action of the one-way clutch F, and the planetary ring gear 16f is locked. to transmit rotational force to However, during engine braking, a reverse force acts, the one-way clutch F does not act, and the planetary carrier 16e idles. Therefore, when the gear stage is the 1st speed and the shift lever is in the L range, the brake B2 is applied to fix the planetary carrier 16e so that the engine braking action can be exhibited.

When the gear stage is the 2nd speed, as shown in FIG. 2, the clutch C2 and the brake B1 are actuated to output rotational force in the forward direction (for example, rightward direction). Specifically, when the gear stage is 2, since the clutch C2 is working, the rotational force of the input shaft 14 is directly transmitted to the rear planetary sun gear 16b and is transmitted to the planetary short pinion 16c in the opposite direction. to transmit the rotational force to the On the other hand, the brake B1 locks the front planetary sun gear 16a. As a result, the planetary long pinion 16d meshing with the planetary short pinion 16c receives a rotational force in the positive direction, revolves in the positive direction on the front planetary sun gear 16a while rotating, and rotates in the positive direction on the planetary ring gear 16f. to transmit the rotational force of The rotational force of the planetary ring gear 16f outputs forward rotational force.

When the gear stage is 3, the clutches C2 and C3 are actuated to output rotational force in the forward direction at a predetermined gear ratio. Specifically, when the gear stage is 3, the input shaft 14, the rear planetary sun gear 16b, and the planetary carrier 16e rotate in the same direction because the clutches C2 and C3 are operating. . Accordingly, the planetary short pinion 16c and the planetary long pinion 16d are locked, and the planetary ring gear 16f receives a positive rotational force and outputs a positive rotational force.

When the gear stage is the 4th stage, the clutch C3 and the brake B1 are operated to output rotational force in the forward direction at a predetermined speed reduction ratio. Specifically, when the gear stage is 4th gear, the clutch C3 is in operation, so the rotational force of the input shaft 14 is directly transmitted to the first output shaft 20, and the planetary carrier 16e moves in the positive direction. to transmit the rotational force of On the other hand, the front planetary sun gear 16a is locked by the action of the brake B1. As a result, the planetary long pinion 16d supported by the planetary carrier 16e revolves on the front planetary sun gear 16a while rotating under the forward rotational force, thereby rotating the planetary ring gear 16f in the forward direction. Rotation of the planetary ring gear 16f outputs rotational force in the positive direction.

When the shift lever is in the R range, the clutch C1 and the brake B2 act to set the reverse gear, and a torque in the reverse direction is output at a predetermined gear ratio. Specifically, when the shift lever is in the R range, the clutch C1 is in operation, so the rotational force of the input shaft 14 is directly transmitted to the front planetary sun gear 16a. On the other hand, the planetary carrier 16e is fixed by the action of the brake B2. Therefore, the forward rotational force transmitted to the front planetary sun gear 16a causes the planetary long pinion 16d to rotate in the reverse direction, outputting a reverse rotational force to the planetary ring gear 16f.

The second planetary gear mechanism 18 is a planetary gear mechanism provided downstream of the first planetary gear mechanism 16 in the power transmission direction. The second planetary gear mechanism 18 includes a second sun gear 18a, a second pinion gear 18b, and a second ring gear 18c. The second planetary gear mechanism 18 can reduce the power input from the first planetary gear mechanism 16 side at a predetermined reduction ratio and output it to the third output shaft 22 .

The first output shaft 20 is provided with an axial hole 20a extending in the axial direction. The axial hole 20a is supplied with oil pressure-fed from an engine-driven pump. A plurality of holes 20b are formed in the first output shaft 20 in the radial direction. The hole 20b communicates with the axial hole 20a. The holes 20b are provided at positions corresponding to the first planetary gear mechanism 16, the clutch C, the brake B, and the like. Therefore, the oil pressure-fed by the pump can be supplied to the first planetary gear mechanism 16, the clutch C, the brake B, etc. through the axial hole 20a and the hole 20b.

<<About the configuration of the second output shaft 21 and the third output shaft 22>>
Hereinafter, the configuration of the integrally supported second output shaft 21 and the third output shaft 22, which is unique to the transmission 10 of the present embodiment, will be described in detail with reference to the drawings.

The second output shaft 21 receives the rotational force output from the planetary ring gear 16 f and outputs the transmitted rotational force to the third output shaft 22 . Therefore, the second output shaft 21 serves as an input shaft for the third output shaft 22 . The second output shaft 21 includes a second output shaft main body portion 21a, a passive portion 21b extending from the second output shaft main body portion 21a to the planetary ring gear 16f, and the like. The rotational force output from the planetary ring gear 16f is transmitted to the second output shaft 21 by being transmitted to the passive portion 21b. When the passive portion 21b receives the rotational force of the planetary ring gear 16f, the second output shaft 21 axially rotates according to the rotation of the planetary ring gear 16f.

The third output shaft 22 is arranged so that the rotation axis thereof substantially coincides with that of the second output shaft 21, and as described later, the rotation force of the second output shaft 21 is transmitted to rotate the shaft. The third output shaft 22 has a recess 22b formed at one end in the axial direction of the third output shaft body portion 22a.

At least part of the second output shaft main body portion 21a of the second output shaft 21 is inserted into the recess 22b of the third output shaft 22 in such a state that the rotation axis of the second output shaft 21 substantially coincides with the rotation axis of the third output shaft 22. be. Inside the recess 22b, the second output shaft 21 and the third output shaft 22 are mutually supported by the bearings 23 and 25 in a state in which differential rotation is allowed, and the rotational force of the second output shaft 21 is applied to the third output shaft 22. It is a configuration that is transmitted to Each bearing 23, 25 is arranged so as to be in contact with the outer peripheral surface of the second output shaft body portion 21a and the inner peripheral surface of the recess 22b. Further, the respective bearings 23 and 25 support the second output shaft 21 and the third output shaft 22 at two points, and are arranged so that their radial directions are substantially perpendicular to the rotation shaft. Therefore, the second output shaft 21 and the third output shaft 22 are restrained from relatively bending and being displaced in the radial direction. In this manner, the second output shaft 21 and the third output shaft 22 function as an integrated shaft in a state in which differential rotation is allowed and radial displacement is suppressed. Bearing 23 and bearing 25 are not fixed to transmission case 24 .

The integrated second output shaft 21 and third output shaft 22 are rotatably supported on the transmission case 24 by bearings 27 and 29 fixed to the transmission case 24 . Specifically, the bearing 27 is fixed to the transmission case 24 via the bearing support portion 24a, and is arranged in contact with the surface of the second output shaft 21, thereby allowing the second output shaft 21 to move toward the transmission case 24. pivot on. The bearing 29 is fixed to the transmission case 24 via the bearing support portion 24b and arranged in contact with the surface of the third output shaft 22 to pivotally support the third output shaft 22 to the transmission case 24 .

As described above, in the transmission 10 of the present embodiment, the differential rotation of the second output shaft 21 and the third output shaft 22 is allowed by the bearings 23 and 25, and radial displacement is suppressed. After being integrated in a state, they are fixed to the transmission case 24 by bearings 27 and 29 so as to be axially rotatable. Since the second output shaft 21 and the third output shaft 22 can be fixed to the transmission case 24 by two bearings 27, 29, the number of bearings 27, 29 fixed to the transmission case 24 is minimized. As a result, restrictions on the degree of freedom in designing the interior of the transmission case 24 are suppressed, and restrictions on the degree of freedom in designing the vehicle or the like on which the transmission 10 is mounted due to the lengthening of the transmission case 24 are suppressed. Further, a recess 22b is provided in the third output shaft 22, the second output shaft 21 is inserted into the recess 22b, and the second output shaft 21 and the third output shaft 22 are mutually supported by bearings 23 and 25 in the recess 22b. Thereby, the size of the structure for supporting the second output shaft 21 and the third output shaft 22 can be minimized. This also suppresses restrictions on the degree of freedom in designing the interior of the transmission case 24, and suppresses restrictions on the degree of freedom in designing the vehicle or the like in which the transmission 10 is mounted due to the lengthening of the transmission case 24.

In this embodiment, an example is shown in which the rotational force of the first output shaft 20 is transmitted to the second output shaft 21 via the first planetary gear mechanism 16, but from the first output shaft 20 to the second output shaft 21 You may make it perform transmission of the rotational force of by arbitrary structures, such as via a bearing.

As described above, in the transmission 10 of the present embodiment, the third output shaft 22 is provided with the recess 22b, the second output shaft 21 is inserted into the recess 22b, and the second output shaft 21 is driven by the bearings 23 and 25 in the recess 22b. An example in which the output shaft 21 and the third output shaft 22 are mutually supported has been described. However, the structure for mutually supporting the second output shaft 21 and the third output shaft 22 is not limited to this, and the supporting structure is appropriately optimized according to the arrangement structure of the second output shaft 21 and the third output shaft 22. be able to.

It is also possible to use other bearings such as bushes in place of at least one of the bearings 23, 25, 27 and 29 in this embodiment. By using the bearings 23, 25, 27, 29, even when the rotation speed of the second output shaft 21 or the third output shaft 22 is high, the shaft can be easily supported so as to be rotatable. Axial movement of the shaft 21 or the third output shaft 22 can be suppressed. However, not only the bearings 23, 25, 27, 29, but also the shaft rotation speed of the second output shaft 21 or the third output shaft 22, other characteristics, or the arrangement efficiency in the transmission case 24, the cost, etc. An optimal bearing can be used as appropriate, taking into account various factors.

In addition, in the present embodiment, an example of using two bearings 23 and 25 to mutually support the second output shaft 21 and the third output shaft 22 was shown, but three or more bearings such as bearings may be used to support the second output shaft 21 and the third output shaft 22. The second output shaft 21 and the third output shaft 22 may be mutually supported. Since the bearings 23 and 25 for mutually supporting the second output shaft 21 and the third output shaft 22 do not need to be fixed to the transmission case 24, even if three or more bearings are used, the degree of freedom in design is less restricted. , the second output shaft 21 and the third output shaft 22 can be supported with each other in a suitable configuration according to the required performance.

The present invention is not limited to the embodiments described above, and those skilled in the art will readily recognize that other embodiments are possible from the teachings and spirit of the claims without departing from the scope of the claims. Yo.

INDUSTRIAL APPLICABILITY The present invention can be suitably used in transmissions in general.

Reference Signs List 10: transmission 20: first output shaft 21: second output shaft 21a: second output shaft body 21b: passive portion 22: third output shaft 22a: third output shaft body 22b: recess 23: bearing 24: Transmission case 24a: bearing support 24b: bearing support 25: bearing 27: bearing 29: bearing

Claims (1)

A transmission case includes a second output shaft , a third output shaft , and a first output shaft capable of transmitting rotational force from one side to the other,
two or more bearings A that are not fixed to the transmission case and are capable of mutually supporting the second output shaft and the third output shaft ;
a bearing B that is fixed to the transmission case and supports the second output shaft ;
a bearing C that is fixed to the transmission case and supports the third output shaft ;
A recess is provided at one end of the second output shaft ,
at least part of the first output shaft is inserted into the recess,
the first output shaft and at least a portion of the bearing A overlap;
A transmission, wherein the first output shaft and at least a portion of the second output shaft overlap in an axial direction.

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