JPH04128559U - Differential device with torque distribution adjustment mechanism - Google Patents

Abstract

(57) [Summary] [Purpose] The present invention relates to a differential device suitable for use in automobile differential gears, etc., and aims to enable adjustment of the torque distribution ratio of the output shaft. [Structure] In the differential device, the input shaft 3, the first output shaft 1, the second output shaft 2, and the above-mentioned first output shaft 1 and second output shaft 2 are connected to the required differential. and a rotation mechanism R interposed between the input shaft 3 and the linkage mechanism S to rotate the linkage mechanism S as a whole.
The rotation mechanism R is configured to include a torque distribution adjustment mechanism T that adjusts the distribution of the torque output to the first output shaft 1 and the torque output to the second output shaft 2. do.

Description

[Detailed explanation of the idea]

0001

[Industrial application field]

The present invention relates to differential devices, particularly for use in automobile differential gears, etc. The present invention relates to a differential device with a torque distribution adjustment mechanism, which is suitable for use.

0002

[Conventional technology]

In conventional automobiles, the differential gear as a differential device is shown in Fig. 14. The first output shaft 1 is connected to the left wheel side and the right wheel side is connected to the first output shaft 1, which is connected to the left wheel side. between the connected second output shaft 2 and the second output shaft 2 connected to the A related linkage mechanism S is interposed.

0003 In order to rotate the linkage mechanism S as a whole, the linkage mechanism S is provided with a rotation mechanism. R is connected.

0004 The rotation mechanism R is rotated by an input shaft 3 linked to the output shaft of the engine. The output shafts 1 and 2 rotate as required as the input shaft 3 rotates. It looks like this.

[0005] Note that the rotation mechanism R is connected to a bevel gear 4 at the end of the input shaft 3 and to this bevel gear 4. A bevel gear 5 that fits together and a connecting fitting 6 fixed to this bevel gear 5 are provided. It is configured.

[0006] The connecting fitting 6 is formed in a U-shape, and its intermediate portion 6A is fixed to the bevel gear 5. The ends 6B and 6C rotate about the axis of the bevel gear 5. It is now possible to

[0007] In addition, the linkage mechanism S includes a bevel gear 11 fixed to the base end of the output shaft 1, and a bevel gear 11 fixed to the base end of the output shaft 1. Bevel gear 12 fixed to the base end of 2, bevel gear 11, and bevel gear 12. It is comprised of bevel gears 7 and 8 that mesh with both of these for coordination. The bevel gears 7 and 8 are connected to both ends of the connecting fitting 6 via the respective rotating shafts 9 and 10. The linkage mechanism S and the rotation mechanism R are connected by being pivoted to 6B and 6C. Ru.

[0008] With such a configuration, when the input shaft 3 rotates, the rotation mechanism R and the linkage mechanism S The output shafts 1 and 2 are rotated via the.

[0009] At this time, the rotation θ1 of the output shaft 1 and the rotation θ2 of the output shaft 2 are the rotations of the bevel gears 7 and 8. By generating the rotations θ7 and θ8, generation of the difference (differential) is allowed.

0010

[Problem that the idea aims to solve]

However, in the case of such a conventional structure, the first and second output shafts The distribution of the transmitted torque is 50%:50%, and the distribution ratio can be adjusted arbitrarily. It can not be changed.

[0011] The present invention was devised in view of these issues, and is designed to improve the torque distribution ratio of the output shaft. The purpose of this invention is to provide a differential device with a torque distribution adjustment mechanism that can be adjusted. do.

0012

[Means to solve the problem]

Therefore, the differential gear with a torque distribution adjustment mechanism of the present invention has a a force shaft, a first output shaft, a second output shaft, the first output shaft and the second output shaft; A linkage mechanism that links the a rotating mechanism interposed between the input shaft and the linking mechanism, and The rotation mechanism outputs a torque to the first output shaft and a torque output to the second output shaft. It is characterized by being equipped with a torque distribution adjustment mechanism that adjusts the torque distribution. It is said that

[0013]

[Effect]

In the above-mentioned differential gear with torque distribution adjustment mechanism of the present invention, the torque distribution adjustment mechanism The distribution of torque output to the first output shaft and the second output shaft is adjusted to the required state. and the differential gear is operated.

[0014]

【Example】

Hereinafter, embodiments of the present invention will be explained with reference to the drawings. Fig. 1 shows a differential gear with a torque distribution adjustment mechanism as a first embodiment of the invention. A schematic vertical cross-sectional view of the main parts, FIG. 2 is a cross-sectional view of the main parts of the torque distribution adjustment mechanism, and FIG. FIG. 4 is a longitudinal sectional view of the main part of the modification, FIG. 4 is a sectional view taken along the line A-A in FIG. 3, and FIG. 5 is another modification 6 is a sectional view taken along arrow B-B in FIG. 5, and FIG. 7 is a longitudinal sectional view of the main part of the FIGS. 8 to 12 are schematic diagrams of torque distribution adjustment as a second embodiment of the present invention. This figure shows a differential gear with a mechanism, and FIG. 8 is a side view of its main parts, and FIG. 9 is a view taken along arrow D-D in FIG. A sectional view, FIG. 10 is a diagram showing the planetary gear mechanism part, and FIG. 11 explains its operation. FIG. 12 is a schematic longitudinal sectional view of the main part showing a modification thereof, and FIG. 13 is a schematic diagram of FIG. 2, and in FIGS. 1 to 13, the same reference numerals as in FIG. shows the part.

[0015] First, the first embodiment of the present invention will be explained. This first embodiment is shown in FIG. 2, and its basic structure is almost the same as the conventional example shown in FIG. Since the configuration is similar to the above, a detailed explanation of this portion will be omitted.

[0016] By the way, in this embodiment, the rotation mechanism R has a torque output to the first output shaft 1 and a A torque distribution adjustment mechanism T adjusts the distribution of torque output to the second output shaft 2. It is provided.

[0017] That is, in this first embodiment, the rotating shafts 9 and 10 in the conventional example are 13, the rotational force of the end 6B of the connecting fitting 6 is transmitted through the adjustment pin 13. It is transmitted as revolving force around the output shafts 1 and 2 of the bevel gear 7. There is.

[0018] Further, the adjustment pin 13 is a ring centered on the rotation (rotation) center of the bevel gear 7. While engaging with the shaped groove 7A, it is inserted through the hole 6D formed in the connecting fitting 6, Its position can be adjusted along the groove 7A of the bevel gear 7.

[0019] Further, a screw 14 is screwed into the end of the adjustment pin 13, and the motor 1 The adjustment pin 13 is moved in the left-right direction in FIG. It is configured to be displaced to.

[0020] The motor 15 is connected to electrodes 16 and 17, and the electrodes 16 and 17 are connected to the casing 1. The module is connected to an external power supply through connection wires 16A and 17A provided through the It is possible to drive the motor 15. Note that this motor 15 may be, for example, For example, a stepping motor is used.

[0021] Further, the electrodes 16 and 17 are connected to a casing 18 facing near the outer circumference of the bevel gear 5. It extends in a ring shape all around the inner peripheral surface, and is connected to the bevel gear 5 and the motor 15. Due to the rotation of the motor side electrodes 16B and 17B, the electrode 16B and the electrode The electrode 16A and the electrode 17B are configured to maintain a connection state between the electrode 17B and the electrode 17A. There is.

[0022] Note that the bevel gears 7 and 8 are externally connected by pins 19 whose both ends are pivotally connected to the center of rotation. The position in the direction is restricted.

[0023] The pin 19 has a support portion 19A extending in the left-right direction in FIG. 19A is pivotally supported on the axes of the output shafts 1 and 2.

[0024] As a result, the bevel gears 7 and 8 maintain the meshing state with the bevel gears 11 and 12. while rotating around the pin 19 and revolution around the axes of the output shafts 1 and 2. It is now possible to do this.

[0025] With the above-described configuration, in this first embodiment, the bevel gear is rotated by the rotation of the input shaft 3. 5 is rotated. The rotation of the bevel gear 5 is controlled by the bevel gears 7 and 8 via the adjustment pin 13. is transmitted as the revolution of the bevel gears 11 and 12 and the rotation of the bevel gears 4 and 5. Rotation corresponding to the ratio is output at the output shafts 1 and 2.

[0026] If a rotational difference is required between the outputs of output shafts 1 and 2, bevel gear Due to the rotation of the wheels 7 and 8 around the pin 19, different rotations are generated on the output shaft 1 and the output shaft 2. The rotation is output.

[0027] By the way, when adjusting the distribution ratio of torque output to output shaft 1 and output shaft 2, Connecting wires 16A and 17A to the motor 15, electrodes 16 and 17, and electrodes 16B and 17 are connected to the motor 15. A required amount of control current is supplied through B to drive the motor 15.

[0028] As a result, the screw 14 is rotated, and the adjustment pin 13 is driven in the left-right direction in FIG. When the adjustment pin is moved, the adjustment pin moves along the groove 7A as shown in FIG.

[0029] When operation is performed in this state, as shown in FIG. 7, the rotational force F of the bevel gear 5 acts on the position of the adjustment pin 13 in the bevel gear 7.

[0030] Therefore, the rotational force F becomes the rotational force F1, F2 corresponding to the arm lengths L1, L2. That's how it works.

[0031] Here, F1=(L2/L)F, F2=(L1/L)F, and L1, L2 are , the meshing points between the adjustment pin 13 and the bevel gear 7 and the bevel gears 11 and 12, respectively. This is the distance to .

[0032] As a result, an output torque corresponding to the rotational force F1 is output to the output shaft 1, and the output shaft 2, an output torque corresponding to the rotational force F2 is output.

[0033] Therefore, by changing the position of the adjustment pin 13, the differential between the output shafts is allowed. The output torque distribution to the output shafts 1 and 2 can be adjusted while .

[0034] Note that the motor 15 is composed of a stepping motor as described above, but this The means for driving the adjustment pin 13 by the motor 15 is as shown in the modified examples of FIGS. 3 and 4. It may be configured as follows.

[0035] That is, in the modification shown in FIGS. 3 and 4, the output shaft 15A of the motor 15 is It is arranged on the axis of the bell gear 7, and the adjustment pin 13 is connected to the output shaft 15A of the motor 15. They are connected via an arm 21.

[0036] Further, the adjustment pin 13 has a disc shape centered on the rotation (autorotation) center of the bevel gear 7. is engaged with the recess 7A' of the bevel gear 7, and its position is in contact with the inner wall of the recess 7A' of the bevel gear 7. It can be adjusted while doing so.

[0037] With such a configuration, in this modification, the position adjustment of the adjustment pin 13 is performed by the motor 1. 5, the output shaft 15A rotates and the arm 21 swings. be revealed.

[0038] In addition, the displacement driving means for the adjustment pin 13 is configured as shown in the modified examples of FIGS. 5 and 6. You may.

[0039] That is, in the modification shown in FIGS. 5 and 6, the motor 15 is located on the casing 18 side. The linking member 20 is driven left and right in FIG. 5 via the screw 14. It is configured so that it can be used.

[0040] The linking member 20 is formed in a ring shape, and a groove 2 is formed over the entire inner peripheral surface of the linking member 20. 0A is formed.

[0041] The distal end of the adjustment pin 13 is engaged with the groove 20A, and the adjustment pin 13 and the linking member 2 The adjustment pin 13 is allowed to move relative to 0, and the adjustment pin 13 is allowed to move relative to the The deviation is adjusted.

[0042] In addition, the adjustment pin 13 in this case is also centered around the rotation (rotation) center of the bevel gear 7. 7A' of the bevel gear 7. It can be adjusted while contacting the inner wall.

[0043] With such a configuration, in this modification, when adjusting the position of the adjustment pin 13, the motor The motor 15 is driven by the required amount. As a result, the linking member 20 is connected via the screw 14. It is driven in the left-right direction in FIG. 5, and the adjustment pin 13 is displaced through the groove 20A.

[0044] Operation is performed in this state, and the revolution of the bevel gear 7 is such that the end of the adjustment pin 13 has a groove. It is allowed to slide within 20A.

[0045] Next, a second embodiment of the present invention will be explained. This second embodiment is shown in FIGS. 10, the structure of the first embodiment is replaced with a planetary gear type, and the structure of the first embodiment is replaced with a planetary gear type. Enables the required differential between output shafts 1 and 2 between output shaft 1 of output shaft 1 and output shaft 2 of second output shaft 2. An interlocking linkage mechanism S' is interposed.

[0046] In order to rotate this linkage mechanism S' as a whole, a rotating machine is attached to the linkage mechanism S'. The structures R' are connected.

[0047] The rotation mechanism R' rotates by an input shaft 3 connected to the output shaft of the engine. The output shafts 1 and 2 rotate as required as the input shaft 3 rotates. It's starting to look like this.

[0048] The rotation mechanism R' includes a gear 4' at the end of the input shaft 3 and a gear 5 that meshes with this gear 4'. ', and a connecting fitting 6' integrally formed with this gear 5'. Ru.

[0049] The connecting fitting 6' is fitted onto the output shaft 2, and the axial center line of the output shaft 2 is the center of rotation. It is designed to be rotated.

[0050] Further, the linkage mechanism S' includes an internally toothed ring gear 11 fixed to the base end of the output shaft 1. ', a gear 12' fixed to the base end of the output shaft 2, a ring gear 11', and a gear 12. A pinion gear 7' is interposed so as to mesh with both of these in order to link the pinion gear 7' with 8', and the pinion gear 7' and the connecting fitting 6' are provided with an adjustment pin. By being connected via the link 13, the linkage mechanism S' and the rotation mechanism R' are connected. ing.

[0051] With such a configuration, when the input shaft 3 rotates, the rotation mechanism R' and the linkage mechanism The output shafts 1 and 2 are rotated via S'.

[0052] At this time, the rotation θ1 of the output shaft 1 and the rotation θ2 of the output shaft 2 are determined by the pinion gear 7', Due to the revolution of 8', the occurrence of the difference (differential) is allowed.

[0053] Next, the rotation mechanism R' calculates the torque output to the first output shaft 1 and the torque output to the second output shaft 2. The torque distribution adjustment mechanism T that adjusts the distribution of torque output to .

[0054] That is, the adjustment pin 13 is centered on its automatic center in the pinion gear 7'. The connecting fitting 6' engages with the ring-shaped groove 7'A formed so as to is inserted into the hole 6'D formed in the It can be adjusted accordingly.

[0055] Further, a screw 14 is screwed into the end of the adjustment pin 13, and a screw 14 is screwed into the end of the adjustment pin 13. The adjustment pin 13 is moved in the direction indicated by the arrow a in FIG. It is configured to be displaced as shown.

[0056] The motor 15 is connected to electrodes 16, 17, which are connected to the casing 18. The motor is connected to an external power supply through connecting wires 16A and 17A provided through the 15 can be driven. In addition, in this case as well, the motor 15 is For example, a stepping motor is used.

[0057] By the way, the electrodes 16 and 17 are connected to the casing 18 facing the outer end surface of the connecting fitting 6'. It extends in a ring shape all around the inner end surface of the gear 5' and the motor 15. Even when the motor side electrodes 16B and 17B rotate due to rotation, the electrode 16B and the electrode 1 6A and electrode 17B and electrode 17A are secured. Ru.

[0058] With the above-described configuration, in this second embodiment, the rotation of the input shaft 3 causes the gears 4', 5' is rotated. The rotation of the gear 5' is controlled by the pinion gears 7' and 7' through the adjustment pin 13. 8' and the rotation of ring gear 11' and gear 12'. Rotation corresponding to a gear ratio of 4'5' is output at the output shafts 1 and 2.

[0059] If a rotation difference is required between the outputs of output shafts 1 and 2, the pinion Due to the rotation of gears 7' and 8', different rotations are output to output shaft 1 and output shaft 2. .

[0060] By the way, when adjusting the distribution ratio of torque output to output shaft 1 and output shaft 2, To do this, the motor 15 is driven by the required amount.

[0061] As a result, the screw 14 is rotated, and the adjustment pin 13 is moved as shown by the arrow b in FIG. It moves along the groove 7'A as shown in FIG.

[0062] When the operation is carried out in this state, the rotational force F of the gear 5' increases as shown in Fig. 11. It acts on the position of the adjusting pin 13 in the pinion gear 7'.

[0063] Therefore, the rotational force F becomes the rotational force F1, F2 corresponding to the arm lengths L1, L2. That's how it works.

[0064] Here, F1=(L2/L)F, F2=(L1/L)F, and L1 , L2 connects the adjustment pin 13 to pinion gear 7' and gears 11' and 12', respectively. This is the distance to the meshing point.

[0065] As a result, an output torque corresponding to the rotational force F1 to the output shaft 1 is output, and an output An output torque corresponding to the rotational force F2 applied to the shaft 2 is output.

[0066] Therefore, also in this second embodiment, the position of the adjustment pin 13 cannot be changed. The output torque distribution to output shafts 1 and 2 can be adjusted while allowing the differential between the output shafts. can be adjusted.

[0067] Note that the driving means for the adjustment pin is configured as shown in the modified examples of FIGS. 12 and 13. Good too.

[0068] That is, in the modification shown in FIGS. 12 and 13, the output shaft 15A of the motor 15 is arranged on the axis of the pinion gear 7', and the adjustment pin 13 is arranged on the output shaft of the motor 15. 15A via an arm 21.

[0069] With such a configuration, in this modification, the position adjustment of the adjustment pin is performed by the motor 15. This is achieved through the rotation of the output shaft 15A and the swinging of the arm 21 by the required amount of drive. It is possible.

[0070] In this second embodiment as well, the adjustment pin 13 is (see Figures 3 and 5) and its position The adjustment may be made while contacting the inner wall of this recess.

[0071]

[Effect of the idea]

As detailed above, according to the differential device with torque distribution adjustment mechanism of the present invention, the input a shaft, a first output shaft, a second output shaft, and the first output shaft and second output shaft. A linkage mechanism that links to enable the required differential, and a rotational drive for the linkage mechanism as a whole. and a rotating mechanism interposed between the input shaft and the linking mechanism. The mechanism outputs torque to the first output shaft and torque output to the second output shaft. This extremely powerful product is equipped with a torque distribution adjustment mechanism that adjusts the torque distribution. With a simple configuration, the torque output to each output shaft can be controlled while allowing differential movement between the output shafts. This has the advantage of being able to adjust the allocation.

[Brief explanation of drawings]

FIG. 1 is a schematic vertical cross-sectional view of main parts in a first embodiment of the present invention.

FIG. 2 is a cross-sectional view of main parts of the torque distribution adjustment mechanism in the first embodiment of the present invention.

FIG. 3 is a vertical sectional view of a main part of a modification of the first embodiment of the present invention.

FIG. 4 is a sectional view taken along the line AA in FIG. 3;

FIG. 5 is a vertical sectional view of a main part of another modification of the first embodiment of the present invention.

6 is a sectional view taken along the line BB in FIG. 5. FIG.

FIG. 7 is a schematic diagram for explaining the operation in the first embodiment of the present invention.

FIG. 8 is a side view of essential parts in a second embodiment of the present invention.

9 is a sectional view taken along the line DD in FIG. 8. FIG.

FIG. 10 is a diagram showing a planetary gear mechanism portion in a second embodiment of the present invention.

FIG. 11 is a schematic diagram for explaining the operation in the second embodiment of the present invention.

FIG. 12 is a schematic vertical cross-sectional view of essential parts showing a modification of the second embodiment of the present invention.

FIG. 13 is a sectional view taken along the line HH in FIG. 12;

FIG. 14 is a schematic vertical cross-sectional view of main parts in a conventional example.

[Explanation of symbols]

1 First output shaft 2 Second output shaft 3 Input shaft 4 Bevel gear 4' gear 5 Bevel gear 5' gear 6,6' Connecting metal fittings 6A Intermediate part of connecting fitting 6B, 6C Both ends of connecting metal fittings 6D, 6'D hole 7 Bevel gear 7A Groove 7A' recess 7' pinion gear 7'A groove 8 Bevel gear 8' pinion gear 9 Rotation axis 10 Rotation axis 11 Bevel gear 11' ring gear 12 Bevel gear 12' gear 13 Adjustment pin 14 screw 15 Motor 16 Electrode 16A connection wire 16B Electrode 17 Electrode 17A connection line 17B Electrode 18 Casing 19 pin 19A Support part 20 Linking member 20A groove 21 Arm R, R' rotation mechanism S, S' linkage mechanism T Torque distribution adjustment mechanism

Claims (1)

[Scope of utility model registration request] Claim 1: In a differential device, an input shaft, a first output shaft, a second output shaft, and the first output shaft and the second output shaft can be differentially operated as required. The apparatus includes a linkage mechanism that links together, and a rotation mechanism that is interposed between the input shaft and the linkage mechanism to rotationally drive the linkage mechanism as a whole, and the rotation mechanism is output to the first output shaft. 1. A differential gear with a torque distribution adjustment mechanism, characterized in that the differential gear includes a torque distribution adjustment mechanism that adjusts the distribution of the torque output to the second output shaft and the torque output to the second output shaft.