JP2003322225A - Three shaft gear device and method for arranging three shaft gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a three shaft gear device which restrains the generation of vibration noise without increasing the number of components and size, and also to provide a method for arranging three shaft gears. <P>SOLUTION: In the three shaft gear device having an input gear 1, which is provided on an input shaft 4, an output gear 3, which is provided on an output shaft 6, and an intermediate gear 2, which is provided on an intermediate shaft 5 and engages with both of the input/output gears 1 and 3, the input shaft 4, the output shaft 6 and the intermediate shaft 5 are arranged so that angle γ between the center line L1 between the shaft center point 7 of the input shaft 4 and the shaft center point 8 of the intermediate shaft 5 and the center line L2 between the shaft center point 8 of the intermediate shaft 5 and the shaft center point 9 of the output shaft 6 becomes an integral multiple of the value obtained by dividing 360° by the number of the teeth of the intermediate gear 2. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is applied to, for example, a transfer device for automobiles, a machine tool, various manufacturing equipment, and the like as a triaxial gear device applied as a drive transmission means between input and output shafts that are separated by a parallel arrangement. And belongs to the technical field of the method for arranging a triaxial gear.

[0002]

2. Description of the Related Art Conventionally, as a triaxial gear device, for example,
The thing described in Unexamined-Japanese-Patent No. 2001-65646 is known.

In this prior art publication, a first intermediate gear and a second intermediate gear that mesh with an input gear and an output gear are provided on an intermediate shaft, and the meshing phase of both intermediate gears is 1
It is described as being arranged so as to proceed with a phase difference of / 2 pitch.

[0004]

However, in the conventional three-axis gear device, when the intermediate gear and the intermediate shaft are integrally formed, the two gears on the intermediate shaft have a 1/2 pitch. It is necessary to cut the gears with a phase difference. Further, when fixing the two intermediate gears of the intermediate shaft, it is necessary to gear the two intermediate gears and then fix them so that the meshing phases on the intermediate shaft have a phase difference of 1/2 pitch. .

Therefore, in any case, the manufacturing cost of the three-axis gear device increases, and since the two intermediate gears are arranged on the intermediate shaft, the axial dimension becomes long and the device becomes large. There was a problem.

The present invention has been made in view of the above problems, and provides a triaxial gear device and a triaxial gear arranging method capable of suppressing the generation of vibration noise without increasing the number of constituent parts or the size. The purpose is to do.

[0007]

In order to achieve the above object, according to the present invention, an input gear provided on an input shaft, an output gear provided on an output shaft, and an input gear provided on an intermediate shaft are provided. In a triaxial gear device having one intermediate gear that meshes with both of the above, a center line connecting the axial center point of the input shaft and the axial center point of the intermediate shaft, and the axial center point of the intermediate shaft and the output shaft. The input shaft, the output shaft, and the intermediate shaft are arranged so that the angle formed by the center line connecting the shaft center point and the center line is an integral multiple of a value obtained by dividing 360 ° by the number of intermediate gear teeth.

Here, regarding the relationship between the "shaft and the gear", the gear may be fixed to the shaft, or the gear and the shaft may be integrally formed.

"A value obtained by dividing 360 ° by the number of teeth of the intermediate gear" means an angle formed by a circumferential pitch (circular pitch) of one tooth of the intermediate gear with respect to the gear center of the intermediate gear.

[0010]

According to the present invention, the angle formed by the two center lines is
Since it is set to be an integer multiple of the value obtained by dividing 360 ° by the number of teeth of the intermediate gear, the meshing of the input gear and the intermediate gear and the meshing of the intermediate gear and the output gear are approximately 1 of the front normal pitch in the direction of the working line. It will proceed with a phase difference of / 2,
The meshing transmission error generated in each meshing portion is canceled out as a periodic function in which the phases are mutually inverted, and the generation of vibration noise can be suppressed.

Therefore, in the present invention, the intermediate gear is 1
Since the individual pieces are used, it is possible to suppress the generation of vibration noise without increasing the number of constituent parts or the size.

[0012]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, an embodiment for realizing a triaxial gear device and a method for arranging a triaxial gear according to the present invention will be described as a first embodiment corresponding to the invention according to claims 1 and 4, and A description will be given based on a second embodiment corresponding to the invention according to 2 and a third embodiment corresponding to the invention according to claim 3.

(First Embodiment) First, the structure will be described. FIG. 1 is a diagram showing a triaxial gear device of the first embodiment. In FIG. 1, 1 is an input gear, 2 is an intermediate gear, 3 is an output gear,
4 is an input shaft, 5 is an intermediate shaft, 6 is an output shaft, 7 is an axial center point of the input shaft 4, 8 is an axial center point of the intermediate shaft 5, 9 is an axial center point of the output shaft 6, and L1 is an axial center point. The center line connecting 7 and 8, L2 is the axial center point 8 and 9.
It is the center line connecting the.

The triaxial gear device of the first embodiment is provided with the input gear 1 provided on the input shaft 4, the output gear 3 provided on the output shaft 6, and the intermediate shaft 5, and the input / output gears. 1,
3 and one intermediate gear 2 that meshes with both. The input shaft 4, the intermediate shaft 5, and the output shaft 6 are rotatably supported by a case (not shown) via bearings or the like.

Then, a center line L1 connecting the axial center point 7 of the input shaft 4 and the axial center point 8 of the intermediate shaft 5, and the axial center point 8 of the intermediate shaft 5 and the axial center point 9 of the output shaft 6 are connected. Angle γ between the center line L2 and
However, the input shaft 4, the output shaft 6, and the intermediate shaft 5 are arranged so as to be an integral multiple of a value obtained by dividing 360 ° by the number of teeth of the intermediate gear 2.

Next, the operation will be described.

[Set to meshing phase difference] First, the center line L1
The angle γ between the center line L2 and the center line L2 is 360
An integer multiple of the value obtained by dividing ° by the number of teeth of the intermediate gear 2 (n times: n =
1, 2, 3, ...) In other words, it is set to be an integral multiple of the angle formed by one front circle pitch (front circle pitch per tooth) of the intermediate gear 2. In other words, there are n teeth of the intermediate gear 2 at the angle γ, and this setting is
This means that the meshing portion A of the input gear 1 and the intermediate gear 2 and the meshing portion B of the intermediate gear 2 and the output gear 3 have the same relative meshing tooth profile.

At the meshing portion A between the input gear 1 and the intermediate gear 2, as shown in FIG. 2, the input gear 1 which transfers the rotational power to the intermediate gear 2 is rotated counterclockwise, so that the input The left flanks of the left and right flanks of the gear 1 and the intermediate gear 2 contact each other to transmit power.

On the other hand, in the meshing portion B between the intermediate gear 2 and the output gear 3, as shown in FIG. 2, the intermediate gear 2 that transfers the rotational power to the output gear 3 is rotated clockwise, so that the intermediate gear 2 is rotated. The right flank of the left and right flanks of 2 and the output gear 3 come into contact with each other to transmit power.

Here, the meshing point at the meshing portion A between the input gear 1 and the intermediate gear 2 is defined as a, and this meshing point a
However, as shown in FIG. 2, when it is on the center line L1, the meshing points b1 and b2 in the meshing portion B of the intermediate gear 2 and the output gear 3 are the action lines connecting both points b1 and b2. The center line L2 is arranged so as to cross the substantially middle position. The line of action is a common tangent line drawn obliquely to the basic circles of both gears 2 and 3, and the tooth flanks contact on this line of action.

Therefore, the front normal pitch between the meshing point b1 and the center line L2 and the front normal pitch between the meshing point b2 and the center line L2 are the lengths of the action lines connecting the meshing points b1 and b2. It is approximately half the front normal pitch. As a result,
The meshing between the input gear 1 and the intermediate gear 2 and the meshing between the intermediate gear 2 and the output gear 3 proceed with a phase difference of approximately 1/2 of the front normal pitch in the direction of the working line.

[Vibration Noise Suppression Action] First, a case will be described in which the meshing of the input gear and the intermediate gear and the meshing of the intermediate gear and the output gear progress with substantially the same phase with almost no phase difference in the action line direction. .

The transmission error characteristic (A) due to the meshing of the input gear and the intermediate gear and the transmission error characteristic (B) due to the meshing of the intermediate gear and the output gear are as shown in the lower part of FIG.
In both transmission error characteristics (A) and (B), the transmission error has a maximum value at a position of approximately 1/2 front normal pitch while moving one front normal pitch, and both ends of one front normal pitch. It shows the characteristic that the transmission error becomes the minimum value at the position.

Therefore, the total transmission error characteristic obtained by adding the transmission error characteristic (A) and the transmission error characteristic (B) is the maximum value and the minimum value of the transmission error characteristic (A) as shown in the upper part of FIG. And a difference between the maximum value and the minimum value of the transmission error characteristic (B) are added to obtain a characteristic having a large fluctuation range. This 2
Due to the synergistic effect of accumulating three meshing transmission errors, a high gear meshing vibration noise is generated.

On the other hand, in the triaxial gear device of the first embodiment, the center line L1 connecting the shaft center point 7 of the input shaft 4 and the shaft center point 8 of the intermediate shaft 5 and the shaft center point of the intermediate shaft 5 are connected. 8 and the shaft center point 9 of the output shaft 6
The input shaft 4 is arranged so that the angle γ formed by the center line L2 connecting between and is 360 ° divided by the number of teeth of the intermediate gear 2.
Since the output shaft 6 and the intermediate shaft 5 are arranged, as described above, the meshing between the input gear 1 and the intermediate gear 2 and the intermediate gear 2
The meshing between the output gear 3 and the output gear 3 progresses with a phase difference of approximately 1/2 of the front normal pitch in the direction of the action line.

As shown in the lower part of FIG. 4, the transmission error characteristic (A) due to the meshing of the input gear and the intermediate gear shows that the transmission error has the maximum value at the position of ta while moving one front normal pitch. Shows the following characteristics. On the other hand, the transmission error characteristic (B) due to the meshing of the intermediate gear and the output gear is as shown in the lower part of FIG.
It shows the characteristic that the transmission error becomes the minimum value at the position of ta.

Therefore, the total transmission error characteristic obtained by adding the transmission error characteristic (A) and the transmission error characteristic (B) is, for example, as shown in the upper part of FIG. 4, the fluctuation of the maximum value of the transmission error characteristic (A). Is canceled by the fluctuation of the minimum value of the transmission error characteristic (B) as a periodic function in which the phases are mutually inverted, and the transmission errors are averaged at each phase position. It is a characteristic with a small fluctuation range. The meshing vibration noise of the gears 1, 2 and 3 is suppressed by the transmission error canceling effect of averaging the two meshing transmission errors.

Next, the effect will be described.

(1) In the three-shaft gear device of the first embodiment, the input gear 1 provided on the input shaft 4, the output gear 3 provided on the output shaft 6, and the intermediate shaft 5 are provided. , A single intermediate gear 2 meshing with both the input / output gears 1 and 3, a center line connecting an axial center point 7 of the input shaft 4 and an axial center point 8 of the intermediate shaft 5. The angle γ formed by L1 and the center line L2 connecting the axial center point 8 of the intermediate shaft 5 and the axial center point 9 of the output shaft 6 is an integral multiple of the value obtained by dividing 360 ° by the number of teeth of the intermediate gear 2. Since the input shaft 4, the output shaft 6, and the intermediate shaft 5 are arranged so as to achieve the above, it is possible to provide a three-axis gear device capable of suppressing the generation of vibration noise without increasing the number of components or the size thereof. .

(2) In the method of arranging the three-axis gear of the first embodiment, the input gear 1 provided on the input shaft 4 and the output shaft 6 are provided.
And an output gear 3 provided on the intermediate shaft 5, and an intermediate gear 2 provided on the intermediate shaft 5 and meshed with both the input / output gears 1 and 3.
In the method of arranging the three-axis gear having the following, a center line L1 connecting the shaft center point 7 of the input shaft 4 and the shaft center point 8 of the intermediate shaft 5, and the shaft center point 8 of the intermediate shaft 5 and the output shaft 6 A center line connecting with the axial center point 9
Since the angle γ formed by L2 and the input shaft 4, the output shaft 6, and the intermediate shaft 5 are arranged such that the angle γ formed by L2 is an integral multiple of a value obtained by dividing 360 ° by the number of teeth of the intermediate gear 2, It is possible to provide a method for arranging a triaxial gear that can suppress the generation of vibration noise without increasing the number of parts or the size.

(Second Embodiment) In the second embodiment, the input gear 1 is used.
And the relative tooth surface shape of the meshing portion A of the intermediate gear 2 and the relative tooth surface shape of the meshing portion B of the intermediate gear 2 and the output gear 3 are the same.

Since the other structure is the same as that of the first embodiment shown in FIG. 1, its illustration and description are omitted.

Next, the operation will be described.

The meshing transmission error at the meshing portion A between the input gear 1 and the intermediate gear 2 and the meshing transmission error at the meshing portion B between the intermediate gear 2 and the output gear 3 vary depending on the relative tooth surface shape.

Therefore, by making the relative tooth surface shapes of both meshing portions A and B equal to each other, the meshing transmission error occurring in both meshing portions A and B can be equalized.

Therefore, the transmission error characteristic (A) due to the meshing of the input gear and the intermediate gear is, for example, as shown in the lower part of FIG.
The characteristic shows that the maximum value of the transmission error is maintained between tb and tc and the minimum value of the transmission error is maintained between td and te. On the other hand, as shown in the lower part of FIG. 5, the transmission error characteristic (B) due to the meshing of the intermediate gear and the output gear shows that the transmission error of the transmission error is, for example, between td and te while moving one front normal pitch. The characteristic is such that the maximum value is maintained and the minimum value of the transmission error is maintained between tb and tc.

Accordingly, the total transmission error characteristic obtained by adding the transmission error characteristic (A) and the transmission error characteristic (B) is, for example, as shown in the upper part of FIG. The fluctuation is canceled out by the minimum value region of the transfer error characteristic (B) and becomes a flat property by the intermediate value, so that they are canceled by the periodic functions in which the phases are mutually inverted, and the transfer error is averaged at each phase position. As a result, the characteristic becomes a fluctuation range smaller than that of the first embodiment as a whole.

Next, the effect will be described. In addition to the effect (1) of the first embodiment, the triaxial gear device of the second embodiment can obtain the following effect.

(3) Since the relative tooth surface shape of the meshing portion A of the input gear 1 and the intermediate gear 2 and the relative tooth surface shape of the meshing portion B of the intermediate gear 2 and the output gear 3 are made equal to each other, it is the same as the first embodiment. In comparison, the generation of vibration noise due to meshing of the gears 1, 2, 3 can be further suppressed.

(Third Embodiment) In the third embodiment, the input gear 1 is used.
Is an example in which the meshing ratio of the meshing portion A of the intermediate gear 2 and the meshing ratio of the meshing portion B of the intermediate gear 2 and the output gear 3 are equal.

Here, the meshing ratio represents the number of teeth meshing at the same time. For example, in the case of a spur gear, since the simultaneous contact line is parallel to the gear rotation axis, the meshing ratio is the front meshing. In the case of a helical gear, since the simultaneous contact line is inclined with respect to the gear rotation axis, the meshing ratio is calculated by the sum of the front meshing ratio and the overlapping meshing ratio.

Since the other structure is the same as that of the first embodiment shown in FIG. 1, its illustration and description are omitted.

Next, the operation will be described.

The mesh transmission error at the mesh portion A between the input gear 1 and the intermediate gear 2 and the mesh transmission error at the mesh portion B between the intermediate gear 2 and the output gear 3 vary depending on the mesh ratio.

Therefore, by setting the meshing ratios of the meshing portions A and B to be equal, the meshing transmission errors occurring in the meshing portions A and B can be equalized.

Therefore, the transmission error characteristic (A) due to the mesh between the input gear and the intermediate gear, the transmission error characteristic (B) due to the mesh between the intermediate gear and the output gear, the transmission error characteristic (A) and the transmission error characteristic (B). As in the case of the second embodiment, the total transmission error characteristic obtained by summing the above and) is a characteristic with a fluctuation range smaller than that of the first embodiment as a whole, as shown in FIG.

Next, the effect will be described. In addition to the effect (1) of the first embodiment, the triaxial gear device of the third embodiment can obtain the following effect.

(4) Since the meshing ratio of the meshing portion A between the input gear 1 and the intermediate gear 2 and the meshing ratio of the meshing portion B between the intermediate gear 2 and the output gear 3 are made equal to each other, when compared with the first embodiment, Further, generation of vibration noise due to meshing of the gears 1, 2, 3 can be suppressed.

The triaxial gear device and the method for arranging the triaxial gear of the present invention have been described above based on the first to third embodiments, but the specific structure is limited to these embodiments. It is not intended that modifications and additions of the design are allowed without departing from the gist of the invention according to each claim of the claims.

For example, in the first to third embodiments, the relationship between the shaft and the gear has been shown by fixing the gear to the shaft, but the gear and the shaft may be integrally formed.

[Brief description of drawings]

FIG. 1 is an overall view showing a triaxial gear device of a first embodiment.

FIG. 2 is an operation explanatory view showing the triaxial gear device of the first embodiment.

FIG. 3 is a transmission error characteristic (A) due to meshing between an input gear and an intermediate gear and a transmission error characteristic (B) due to meshing between an intermediate gear and an output gear in a triaxial gear device having a phase difference of substantially zero.
FIG. 6 is a diagram showing a total transmission error characteristic obtained by adding the transmission error characteristic (A) and the transmission error characteristic (B).

FIG. 4 is an input gear in the three-axis gear device of the first embodiment.
Transmission error characteristics due to meshing of intermediate gears (A) and transmission error characteristics due to meshing of intermediate gears and output gears (B)
FIG. 6 is a diagram showing a total transmission error characteristic obtained by adding the transmission error characteristic (A) and the transmission error characteristic (B).

FIG. 5 shows a transmission error characteristic (A) due to meshing between an input gear and an intermediate gear and a transmission error characteristic (B) due to meshing between an intermediate gear and an output gear in the three-axis gear device of the second and third embodiments. FIG. 6 is a diagram showing a total transmission error characteristic obtained by adding the transmission error characteristic (A) and the transmission error characteristic (B).

[Explanation of symbols]

1 input gear 2 Intermediate gear 3 output gears 4 input axes 5 Middle axis 6 Output shaft 7 Input shaft 4 axis center point 8 Center point of intermediate shaft 5 9 Output shaft 6 center point Center line connecting L1 axis center points 7 and 8 Center line connecting L2 axis center points 8 and 9 γ Angle between center line L1 and center line L2

Claims (4)

[Claims] 1. An input gear provided on an input shaft, an output gear provided on an output shaft, and one intermediate gear provided on an intermediate shaft and meshing with both the input and output gears.
In the shaft gear device, an angle formed by a center line connecting the shaft center point of the input shaft and the shaft center point of the intermediate shaft and a center line connecting the shaft center point of the intermediate shaft and the shaft center point of the output shaft is , 360 ° divided by the number of intermediate gear teeth, an input shaft, an output shaft, and an intermediate shaft are arranged so as to be an integral multiple. 2. The triaxial gear device according to claim 1, wherein a relative tooth surface shape of a meshing portion of the input gear and the intermediate gear is equal to a relative tooth surface shape of a meshing portion of the intermediate gear and the output gear. A three-axis gear device characterized in that 3. The triaxial gear device according to claim 1, wherein a meshing ratio of a meshing portion between the input gear and the intermediate gear,
A triaxial gear device, wherein the meshing ratios of the meshing portions of the intermediate gear and the output gear are made equal. 4. An input gear provided on an input shaft, an output gear provided on an output shaft, and one intermediate gear provided on an intermediate shaft and meshing with both the input and output gears.
In the arrangement method of the shaft gear device, a center line connecting the shaft center point of the input shaft and the shaft center point of the intermediate shaft, and a center line connecting the shaft center point of the intermediate shaft and the shaft center point of the output shaft, A method for arranging a triaxial gear, wherein the input shaft, the output shaft, and the intermediate shaft are arranged such that the angle formed is an integer multiple of a value obtained by dividing 360 ° by the number of intermediate gear teeth.