JPH028537A - Low-noise gear device - Google Patents

Abstract

PURPOSE:To decrease a gear noise by arranging each gear shaft in a manner, wherein a phase difference on a work line of meshing between 1 and 2-shaft gears and between 2 and 3-shaft gears is formed to a half of the transverse base pitch, in the case of a three-shaft parallel gear device having the 1 and 3-shaft gears of equal number of teeth. CONSTITUTION:Vibration by meshing a helical gear 1a of 1-shaft with a helical gear 2a of 2-shaft and vibration by meshing the helical gear 2a of the 2-shaft with a helical gear 3a of 3-shaft are generated. Since a changing period of spring rigidity of a tooth, causing these vibrations, corresponds to the transverse base pitch 7a, a phase difference on a work line of meshing between the gear 1a of the 1-shaft and the gear 2a of the 2-shaft and between the gear 2a of the 2-shaft and the gear 3a of the 3-shaft is set to 1/2 times the transverse base pitch 7a on the same work line 5b. In this way, also a waveform of spring rigidity of the tooth, causing the vibration, mutually generates a 1/2 period phase-shifted function, obtaining the waveform of reverse phase so as to mutually negate both the vibrations, and a gear noise is decreased as a device total unit.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a low-noise gear device applied to automobile transmissions and the like.

(Prior Art) As a conventional low-noise gear device, one shown in FIG. 13 is known.

This conventional low-noise gear system has single-axis gears 101 and 3.
Two shaft gears 102 mesh with shaft gears 103, respectively.
A buffer member 1 is installed in the hough portion 105 between the gear shaft 104 and
By interposing 06, the vibration caused by the meshing of the gears is alleviated.

(Problem to be solved by the invention) However, in such a conventional low-noise gear device, the vibration caused by meshing of the gears is alleviated by the buffer member 106 interposed in the huff portion 105. Therefore, this buffer member 106 reduces the strength of the hub portion 105, making it impossible to transmit high-load power, and
To the huff section +05&l? Processing for interposing the ii member 106 is troublesome, and there are problems such as increased costs.

The present invention has focused on the above-mentioned problems, and has been developed to reduce vibration ( A common issue is the development of low-noise gear devices that can reduce gear noise (gear noise).

(Means for Solving the Problems) In order to solve the above problems, a low noise gear device according to claim 1 is provided with a gear on one shaft meshing with the gears on two shafts, and three gears meshing with the gears on two shafts.
In a three-axis parallel gear device in which the gears on the shaft and the gears have the same number of teeth, the phase difference on the line of action between the meshing between the gears on the one shaft and the gears on the second shaft and the meshing between the gears on the second shaft and the gears on the third shaft. but,
The means is characterized in that each gear shaft is arranged at 1/2 of the front normal pitch.

Further, in the low noise gear device according to claim 2, in a planetary gear device having an even number of planetary gears meshing with the sun gear, an arbitrary half of the planetary gears and the sun gear among the even number of planetary gears are provided. The means is characterized in that each planetary gear is arranged so that the phase difference on the line of action between the meshing and the meshing of the remaining half of the planetary gears and the sun gear is 1/2 of the front normal pitch.

Further, in the low noise gear device according to claim 3, in the three-axis parallel gear device in which the number of teeth of the one-axis gear and the three-axis gear that mesh with the two-axis gears are different, the one-axis gear and the two-axis gear are meshed with the two-axis gears. In addition to matching the meshing ratio of the gears on the shaft with the meshing ratio of the gears on the second and third axes, the meshing between the gears on the first and second axes and the meshing between the gears on the second and third axes is also adjusted. The method for achieving the special price is to arrange each gear shaft so that the phase difference on the line of action with the front normal pitch is 1/2.

Further, in the low noise gear device according to claim 4, two gears having the same number of teeth provided on the two gear shafts, and a gear on the single shaft and a gear on the third shaft that mesh with each other have the same number of teeth. In an axis-parallel gear device, the phase difference on the line of action between the meshing of the gear on the 1st shaft and one gear on the 2nd shaft and the meshing between the other gear on the 2nd shaft and the gear on the 3rd shaft is the front normal pitch 1/ The means is characterized in that the phases of both gears of the two axes are shifted from each other so that the ratio is 2.

Further, in the low noise gear device according to claim 5, one
In a 3-axis parallel gear device in which the number of teeth of the gear on the 1st axis and the gear on the 3rd axis is different, the engagement ratio between the gear on the 1st axis and one gear on the 2nd axis, and the meshing ratio between the other gear on the 2nd axis and the gear on the 3rd axis. In addition to matching the meshing ratio of the gears, the phase difference on the line of action between the meshing of the gear on the 1st shaft and one gear on the 2nd shaft and the meshing of the other gear on the 2nd shaft is equal to the front normal pitch 1/2. This means is characterized by shifting the phases of both gears of the two axes so that

(Function) In the low-noise gear device according to claim 1, vibrations occur due to the meshing of the gears on the 1st axis and the gears on the 2nd axis, and vibrations due to the meshing between the gears on the 2nd axis and the gears on the 3rd axis. The period of variation in the spring stiffness of the teeth, which causes vibration, corresponds to the front normal pitch, so it is on the line of action between the meshing of the gears on the 1st axis and the gears on the 2nd axis, and the meshing between the gears on the 2nd axis and the gears on the 3rd axis. By setting the phase difference of This results in a waveform with an opposite phase, and gear noise as a whole in a 3-axis parallel gear device in which the number of teeth of the 1-axis gear and the 3-axis gear is the same is reduced.

Further, in the low noise gear device according to claim 2, vibrations caused by meshing between an arbitrary half of the planetary gears and the sun gear among the even number of planetary gears and vibrations caused by meshing between the remaining half of the planetary gears and the sun gear are mutually suppressed. The waveforms have opposite phases so as to cancel each other out, and the gear noise of the entire planetary gear apparatus is reduced.

In addition, in the low noise gear device according to claim 3, the meshing ratio between the gear on the 1st shaft and the gear on the 2nd shaft is made to match the meshing ratio between the gear on the 2nd shaft and the gear on the 3rd shaft. Even in a 3-axis parallel gear device in which the gears and the 3-axis gears have different numbers of teeth, there are vibrations caused by the meshing of the 1-axis gear and the 2-axis gear, and 2-axis gears.
The vibrations caused by the meshing of the gears on the shaft and the gears on the three shafts become waveforms with opposite phases so as to cancel each other out, and the gear noise of the entire device is reduced.

In the low-noise gear device according to claim 4, the one-axis gear and the three-axis gear mesh with two gears having the same number of teeth provided on the two-axis gear, respectively, due to a phase shift between the two gears on the two-axis. Even in a 3-axis parallel gear device with the same number of teeth as
The vibrations caused by the meshing of the gear on the 1st axis and one of the gears on the 2nd axis, and the vibrations caused by the meshing between the other gear on the 2nd axis and the teeth/wheels of the 3rd axis cancel each other out, resulting in waveforms with opposite phases, which damage the entire device. gear noise is reduced.

Further, in the low noise gear device according to claim 5, the meshing ratio between the gear on the 1st shaft and one gear on the 2nd shaft is made to match the meshing ratio between the other gear on the 2nd shaft and the gear on the 3rd shaft. in,
Even in a three-axis parallel gear device in which a single-axis gear and a three-axis gear that mesh with two gears having the same number of teeth provided on two gear shafts and a three-axis gear have different numbers of teeth, the same applies to the case of the invention described in item 4. Similarly, both vibrations have waveforms with opposite phases that cancel each other out, and the gear noise of the entire device is reduced.

(Example) Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

First, the configuration of the first embodiment will be explained.

1 to 3 correspond to the invention set forth in claim 1.

1 is an explanatory diagram showing a low-noise gear device A1 of a first embodiment, in which a single helical gear 1a and a three-axis helical gear 3a mesh with a two-axis helical gear 2a, respectively. It is a three-axis parallel gear device in which the number of teeth is the same, and one gear shaft 1b, two gear shafts 2b, and three gear shafts 3b are arranged in parallel. .

As shown in FIG. 3, there is a simultaneous contact line 4a indicating the meshing state of the helical gear 1a on the 1st shaft and the helical gear 2a on the 2nd shaft, and a line of simultaneous contact between the helical gear 2a on the 2nd shaft and the helical gear 2a on the 3rd shaft. Gear 3a
The same line of action 5 with the simultaneous contact line 5a showing the engaged state of
The phase difference 6a on b is the front eye normal pitch (tes) 7
Each gear shaft 1b, 2b, 3b is arranged so as to be 1/2 of a.

That is, the center point ○l, 0 of the three gear shafts 1b, 2b, 3b
The gear shafts 1b, 2b, and 3b are arranged so that the angle Y formed by the angle 2103 is Z2: number of teeth of the two-axis helical gear 2a, n: an integer.

Here, δ is given by the following formula.

V92: Basic circle radius tes of 2-axis helical gear 2a:
Front normal pitch In Fig. 3, 4b is the line of meshing action between the helical gear 1a on one shaft and the helical gear 2b on two shafts, 4C is the meshing length, and 5b is the helical gear on two shafts. Gear 2 and 3-axis helical gear 3
The meshing action line with a, 5C is the same meshing length, 2C is the base circle of the two-axis helical gear 2a, 2d is the same tip circle, 1C
is the base circle of the 1-axis helical gear 1a, and 3C is the base circle of the 3-axis helical gear 3.

Next, the effect will be explained.

In the three-axis parallel gear device as in this embodiment, vibrations due to meshing between the one-axis helical gear 1a and the two-axis helical gear 2a, and the two-axis helical gears 2a and 3 are generated. Vibration occurs due to the shaft meshing with the helical gear 3a.

The cause of this vibration is the variation in the spring stiffness of the teeth, which is based on the change in the distance between the contact point of the teeth and the center point of the gear, which move as the gears mesh. As shown in Figure 4, it forms a periodic function, and its period is equal to the front normal pitch (
tes) corresponds to 7a.

In Fig. 4, 8 indicates the waveform of the tooth spring stiffness K due to the meshing of the 1-axis helical gear 1a and the 2-axis helical gear 2a, and 9 indicates the waveform of the tooth spring stiffness K due to the meshing of the 1-axis helical gear 1a and the 2-axis helical gear 2a. The lines 2a and 3 axes show the waveform of the spring stiffness of the teeth due to meshing with the gear 3.

On the other hand, the simultaneous contact line 5 days, which indicates the state of meshing between the helical gear 1a on the 1st shaft and the helical gear 2a on the 2nd shaft, is the same line of action 5b as the front normal pitch (tes) 7a. Since a phase difference of 1/2 is provided, the waveforms 8 and 9 of the spring stiffness K of the teeth also become functions that are shifted in phase by 1/2 period.

Therefore, the helical gear 1a on one shaft and the helical gear 2a on two shafts
Vibration due to meshing with the two-axis helical gears 2a and 3
The helical axis of the shaft has a waveform with opposite phases so that vibrations caused by meshing with the gear 3a cancel each other out, and the meshing vibration (gear noise) of the gears in the entire gear device is reduced.

As explained above, in the low noise gear device A1 of the first embodiment, the meshing of the helical gear 1a on the 1st shaft and the helical gear 2a on the 2nd shaft, and the meshing of the helical gear 2a on the 2nd shaft. Since the gear shafts 1b, 2b, and 3b are arranged so that the phase difference on the line of action between the meshing of the helical gear 3a of the 3rd shaft and the helical gear 3a is 1/2 of the front normal pitch (tes) 7a, In a 3-axis parallel gear device in which the helical gear 1a on the shaft and the helical gear 3a on the 3-shaft have the same number of teeth, the meshing vibration of the entire device (
gear noise) can be reduced.

In addition, as mentioned above, each gear shaft ib,
Since this can be achieved by simply changing the arrangement of 2b and 3b, it will not have a negative effect on the strength of the members or the power transmission force, and will not increase costs due to the addition of new members or processing steps.

Next, a second example will be described.

Claim 2gc! As shown in FIGS. 5 and 6, the low noise gear device A2 of the second embodiment corresponding to the invention described above has four planetary gears +1.12 meshing with the sun gear 10, respectively.
．． It is a planetary gear device, that is, a 5-axis parallel gear device, in which the number of teeth of 13 and 14 are all the same.

In the figure, reference numeral 15 indicates a link-shaped internal gear, and each type of gear is a helical gear.

A simultaneous contact line 16 showing the meshing state of the first planetary gear 11 and the third planetary gear 13 with the sun gear 10 and a simultaneous contact line 16 showing the meshing state of the second planetary gear 12 and the fourth planetary gear 14 with the sun gear 10 are also shown. The planetary gears M, 12, 13, and 14 are arranged so that the phase difference 6b on the same line of action 12b with the contact line 17 is 1/2 of the front normal pitch (tes) 7b.

That is, in this embodiment, the first planetary gear 11 and the sun gear 1
0 and the center point 0O102 of the second 'fi star gear 12, and the center point ○ of the third planetary gear 13, the sun gear 10, and the fourth planetary gear 14.

The planetary gears 11', 12, 13, and 14 are arranged so that the angle Y of 0.04 is as in the first embodiment, Zs: number of teeth of the sun gear 10, n: an integer. .

Here, δ is given by the following formula.

Y9S: Base circle radius of the sun gear 10 tes: Front normal pitch In addition, +1b, 12b, 13b, and 14b in FIG. 6 are the respective planetary gears! , 12, 13. 14 and the meshing action line of the sun gear 10, 10a is the base circle of the sun gear 10, lla,
12a, 13a, and 14a are base circles of each planetary gear.

Therefore, in the low noise gear device A2 of this embodiment,
The vibrations caused by the meshing of the first planetary gear 11 and the third planetary gear 13 with the sun gear 10 and the vibrations caused by the meshing of the second planetary gear 12 and the fourth planet with the sun gear 10 cancel each other out. The waveform becomes as follows, and the meshing vibration (gear noise) of the gears in the planetary gear system is reduced.

Incidentally, by applying the relationship with the sun gear 10 in this embodiment to the relationship with the ring-shaped internal gear 15, vibrations caused by meshing with the ring-shaped internal gear 15 can be reduced, but each planetary gear 11. 12, 13, and 14 is larger in relation to the ring-shaped internal gear 15 than in the relation to the sun gear 10, and fluctuations in the spring stiffness of the teeth are smaller. The noise prevention effect will be higher if conditions are set according to the relationship.

Next, a third example will be described.

As shown in FIGS. 7 to 9, a low-noise gear device A3 according to a third embodiment of the present invention, which corresponds to the invention set forth in claim 3, includes a uniaxial helical gear that meshes with two helical gears 2a, respectively. 1a and the three-axis helical gear 3a have different numbers of teeth, and one gear shaft 1b, two gear shafts 2b, and three gear shafts 3.
3-axis parallel gears are arranged parallel to each other.

In this embodiment, since the number of teeth of the helical gear 1a on one axis and the helical gear 3a on three axes is different, in particular, one
The meshing ratio between the helical gear 1a on the shaft and the helical gear 2a on the two shafts, and the helical gear 2a on the two shafts and the helical gear 3a on the third shaft
The meshing ratio is formed so that both the frontal meshing ratio and the overlapping meshing ratio are equal, and 1
A simultaneous contact line 4a showing the meshing state between the helical gear 1a on the shaft and the helical gear 2a on the two shafts, and a simultaneous contact line 4a showing the meshing state between the helical gear 2a on the two shafts and the helical gear 3a on the third shaft. Each gear shaft 1b is adjusted so that the phase difference 6a on the same line of action 5b with the contact line 5a is 1/2 of the front normal pitch (tes) 7c.
, 2b, and 3b are arranged.

That is, the center points 01 and 0 of the three gear axes +b, 2b, and 3b
The angle Y formed by 2.03 is Z2: number of teeth n of the two-axis helical gear 2a, integer V92: base circle radius tes of the two-axis helical gear 2a:
Each gear shaft 1b, 2b, 3b is arranged so as to have a front normal pitch mo and a module.

In Fig. 9, 4b is the line of meshing action between the 1-axis helical gear 1a and the 2-axis helical gear 2a, 4C is the meshing length, and 5b is the meshing action line between the 1-axis helical gear 1a and the 2-axis helical gear 2a. 3-axis helical gear 3
5c is the same meshing length, 2C is the base circle of the 2-axis helical gear 2a, 1C is the base circle of the 1-axis helical gear 1a, 3C is the 3-axis helical gear This is the base circle of 3a.

Therefore, in the low noise gear device A3 of this embodiment,
The meshing ratio between the helical gear 1a on the 1st shaft and the helical gear 2a on the 2nd shaft, and the helical gear 2a on the 2nd shaft and the helical gear 3 on the 3rd shaft.
Since the gears are formed so that the meshing ratio with the gears 1a and 3 are equal in both the frontal meshing ratio and the overlapping meshing ratio, which determine the spring stiffness variation of the teeth that causes vibration due to the meshing of the gears, the uniaxial helical gears 1a and 3 Even in a 3-axis parallel gear device in which the helical shaft has a different number of teeth than the gear 3a, vibrations due to meshing between the helical gear 1a on the 1st shaft and the helical gear 2a on the 2nd shaft, and the helical gear 3a on the 2nd shaft. The vibration caused by the meshing of the gear 2a and the three-axis helical gear 3a can be made into waveforms with opposite phases so that they cancel each other out, and the meshing vibration (gear noise) of the gears as a whole gear device can be reduced. become.

Next, a fourth example will be described.

As shown in FIGS. 10 and 11, the low-noise gear device A4 of the fourth embodiment, which corresponds to the invention of claim 4, has two gear shafts with the same number of teeth provided on the two gear shafts 2b. Helical gear 2a
, 2e, the uniaxial helical gear 1a and the triaxial helical gear 3a have the same number of teeth, forming a three-axis parallel gear device.

In this embodiment, the center point 01. of each gear shaft 1b, 2b, 3b. When the angle Y formed by Oz, 03 is, the meshing of the helical gear 1a of the 1st shaft and the helical gear 2a of the 2nd shaft, the meshing of the helical gear a of the 2nd shaft, and the meshing of the helical gear 2a of the 2nd shaft, Both helical gears 2a with two axes so that the phase difference between the meshing of the helical gear 2e and the helical gear 3a with three axes on the same line of action is 1/2 of the front normal pitch (tes), 2e are provided with mutual phases shifted.

That is, as shown in FIG. 11, both gears 2a and 2e are arranged so that the phase difference n between the tooth profile 20a of one gear 2a and the tooth profile 20e of the other gear 2e of the two shafts is as follows.

Therefore, the same effects as in the first embodiment can be obtained in this embodiment as well.

Next, a fifth example will be described.

The low-noise gear system of the fifth embodiment corresponding to the invention as claimed in claim 5 [A5 has a different number of teeth between the 1-axis helical gear 1a and the 3-axis helical gear 3a as shown in FIG. Other than that,
This is a three-axis parallel gear device similar to the low noise gear device A4 of the fourth embodiment.

Therefore, in addition to the conditions in the fourth embodiment, the meshing ratio between the helical gear 1a on the 1st shaft and the helical gear 2a on the 2nd shaft, the helical gear 2e on the other shaft on the 2nd shaft, and the helical gear 2e on the 3rd shaft. By adding the condition that the engagement ratio of the helical gear 3a and the helical gear 3a match, the same effect as in the fourth embodiment can be obtained.

Although the embodiments of the present invention have been described above in detail with reference to the drawings, the specific configuration is not limited to these embodiments, and the present invention may be modified without departing from the gist of the present invention. include.

For example, in the embodiment, a case where a helical gear is used is shown, but the type of gear may be arbitrary.

(Effects of the Invention) As explained above, in the low noise gear device according to claim 1, the meshing of the gear on one shaft and the gear on two shafts,
Each gear shaft is arranged so that the phase difference on the line of action between the meshing gears of the 2nd shaft and the 3rd shaft is 1/2 the front normal pitch, so there is no negative effect on the strength of the members or power transmission. , and the number of teeth of the gears on one shaft and the gears on three shafts that mesh with the gears on two shafts are the same, without increasing the cost due to the addition of new parts or processing steps3.
Vibration (gear noise) in fine gear gears can be reduced.

In addition, in the low noise gear device according to claim 2, the meshing between an arbitrary half of the planetary gears and the sun gear among the even number of planetary gears, and the meshing between the remaining half of the planetary gears and the sun gear. Because each planetary gear is arranged so that the phase difference on the line of action is 1/2 of the front normal pitch, there is no negative effect on component strength or power transmission, and the cost of adding new components and processing steps is reduced. It is possible to reduce vibration (gear noise) in a planetary gear device having an even number of planetary gears each meshing with a sun gear without overlapping.

In addition, in the low-noise gear device according to claim 3, the meshing ratio between the gears on one shaft and the gears on two shafts is made to match the meshing ratio between the gears on two shafts and the gears on three shafts, and The phase difference on the line of action between the meshing between the gears and the gears on the two axes and the meshing between the gears on the two axes and the three axes is equal to the front normal pitch 1/
Since each gear shaft is arranged so that the number of gears is 2, it is possible to create a 2-axis structure without adversely affecting the strength of the parts or power transmission, and without increasing costs due to the addition of new parts or machining processes. It is possible to reduce vibration (gear noise) in a three-fine hand gear device in which the number of teeth of the one-axis gear and the three-axis gear that mesh with the gears is different.

In addition, in the low noise gear device according to claim 4, on the line of action between the gear of one shaft and one of the gears of two shafts, and the meshing of the other gear of two shafts and the gear of three shafts, Because the phases of both gears on the two axes are shifted so that the phase difference is 1/2 of the front normal pitch, there is no negative effect on component strength or power transmission, and the addition of new components and processing steps can be avoided. Without increasing costs, the gears on the 1st and 3rd shafts are meshed with two gears with the same number of teeth on the 2nd gear shaft. Vibrations (gear noise) in gear devices can be reduced.

In the low-noise gear device according to claim 5, the meshing ratio between the gear on the 1st shaft and one gear on the 2nd shaft is made equal to the meshing ratio between the other gear on the 2nd shaft and the gear on the 3rd shaft. At the same time, the phase difference on the line of action between the meshing of the gear on one shaft and the gear on the second shaft and the meshing of the other gear on the two shafts is
Since the phases of both gears on the two axes are shifted so that the front normal pitch is 1/2, there is no negative effect on component strength or power transmission, and cost increases due to the addition of new components and processing steps are avoided. Vibrations in 3-axis parallel gears (gears noise) can be reduced.

[Brief explanation of the drawing]

Fig. 1 is a side view showing a low-noise gear device according to the first embodiment of the present invention, Fig. 2 is an overall layout of the gear, Fig. 3 is an explanatory diagram showing details of the meshing situation of the gear, and Fig. 4. 5 is a diagram showing the change in tooth spring stiffness over time, FIG. 5 is an overall layout diagram of a gear showing the second embodiment of the present invention, FIG. 6 is an explanatory diagram showing details of the meshing situation of the same gear, and FIG. 8 is a side view showing the third embodiment of the present invention, FIG. 8 is an overall layout diagram of the same gear, FIG. 9 is an explanatory diagram showing details of the meshing situation of the same gear, and FIG. 10 is a fourth embodiment of the present invention. FIG. 11 is an explanatory diagram showing the phase shift state of the same gear, FIG. 12 is a side view showing the fifth embodiment of the present invention, and FIG. 13 is an explanatory diagram showing a conventional low-noise gear device. be. 1...1 shaft helical gear 2a...2 shaft helical gear 3a...3 shaft helical gears 4b, 5b...line of action 7a...front normal pitch O. ...Sun gear 1...First planetary gear 2...Second planetary gear 3...Third planetary gear 4...Fourth planetary gear 7b...Front normal pitch Mb, +2b, 13b, 14b...-line of action time Fig. 10 A = / / Fig. 12

Claims (1)

[Scope of Claims] 1) In a 3-axis parallel gear device in which the number of teeth of the 1-axis gear and the 3-axis gear that mesh with the 2-axis gears is the same, the 1-axis gear and the 2-axis gear A low-noise gear device characterized in that each gear shaft is arranged so that the phase difference on the line of action between the meshing of the two-axis gear and the third-axis gear is 1/2 of the front normal pitch. . 2) In a planetary gear system having an even number of planetary gears each meshing with a sun gear, of the even number of planetary gears, any half of the planetary gears mesh with the sun gear, and the remaining half of the planetary gears mesh with the sun gear. A low-noise gear device characterized in that each planetary gear is arranged so that the phase difference on the line of action with respect to the meshing of the gears is 1/2 of the front normal pitch. 3) In a 3-axis parallel gear device in which the number of teeth of the 1-axis gear and the 3-axis gear that mesh with the 2-axis gears is different, the meshing ratio of the 1-axis gear and the 2-axis gear, and the 2-axis gear In addition to matching the meshing ratio of the gear and the gears of the three axes,
Each gear shaft is arranged so that the phase difference on the line of action between the gear on the shaft and the gear on the second shaft and the gear on the second shaft and the third shaft is 1/2 the front normal pitch. A low-noise gear device featuring: 4) In a three-axis parallel gear device in which two gears with the same number of teeth are provided on two gear shafts, and a one-axis gear and a third-axis gear that mesh with each other have the same number of teeth, the one-axis gear and 2
The mutual phase of both gears on the two axes is adjusted so that the phase difference on the line of action between the meshing of the gears on one of the shafts and the meshing of the other gear on the two shafts and the gear on the third shaft is 1/2 the front normal pitch. A low-noise gear device characterized by shifted. 5) In a 3-axis parallel gear device in which the 1-axis gear and the 3-axis gear mesh with two gears with the same number of teeth provided on the 2-axis gear shafts, the 1-axis gear and the 3-axis gear have different numbers of teeth. The meshing ratio of one gear on one shaft and the other gear on two shafts and 3
In addition to matching the meshing ratio of the gears on the shaft, the phase difference on the line of action between the meshing of the gear on one shaft and one gear on the two shafts and the meshing of the other gear on the two shafts is set to the front normal pitch 1/ 1. A low-noise gear device characterized in that the phases of both gears of two axes are shifted from each other so that the gears are shifted in phase.