JPH028537A - Low-noise gear device - Google Patents
Low-noise gear deviceInfo
- Publication number
- JPH028537A JPH028537A JP15636088A JP15636088A JPH028537A JP H028537 A JPH028537 A JP H028537A JP 15636088 A JP15636088 A JP 15636088A JP 15636088 A JP15636088 A JP 15636088A JP H028537 A JPH028537 A JP H028537A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- shaft
- axis
- gears
- meshing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000003247 decreasing effect Effects 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 10
- 238000010586 diagram Methods 0.000 description 9
- 230000005540 biological transmission Effects 0.000 description 7
- 230000010363 phase shift Effects 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
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Abstract
Description
【発明の詳細な説明】
(産業上の利用分野)
本発明は、自動車用変速機等に適応される低騒音歯車装
置に関する。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.
(従来の技術)
従来の低騒音歯車装置としては、第13図に示すような
ものが知られている。(Prior Art) As a conventional low-noise gear device, one shown in FIG. 13 is known.
この従来の低騒音歯車装置日は、1軸の歯車101と3
軸の歯車103とがそれぞれ噛み合う2軸の歯車102
と、該歯車軸104との間のハフ部105に緩衝部材1
06を介装させることによって、歯車の噛み合いによる
振動を緩和するようにしている。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.
(発明か解決しようとする課題)
しかしながら、このような従来の低騒音歯車装置にあっ
ては、ハフ部105に介装した緩衝部材106によって
歯車の噛み合いによる振動を緩和するようにしたもので
ある為、この緩衝部材106によってハブ部105の強
度か低下し、高負荷の動力伝達ができなくなると共に、
ハフ部+05へ&l?ii部材106を介装させるため
の加工が面倒であり、コストアップになる等の問題があ
る。(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.
本発明は、上記のような問題に着目し、部材強度や動力
伝達に悪影響を及ぼすことなく、且つ、新たな部材や加
工工程の追加によるコストアップを生ゼしめることなし
に歯車装置における振動(歯車騒音)を低減化すること
ができる低騒音歯車装置の開発を共通の課題とする。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).
(問題点を解決するための手段)
上記課題を解決するために請求項1記載の低騒音歯車装
置では、2軸の歯車にそれぞれ噛み合う1軸の歯車と3
軸の歯車との歯数が同一である3軸平行歯車装置におい
て、前記1軸の歯車と2軸の歯車の噛み合いと、2軸の
歯車と3軸の歯車の噛み合いとの作用線上の位相差が、
正面法線ピッチの1/2となるように各歯車軸を配置し
たことを特徴とする手段とした。(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.
また、請求項2記載の低騒音歯車装置では、太陽歯車に
それぞれ噛み合う偶数個の遊星歯車を有する遊星歯車装
置において、前記偶数個の遊星歯車装置のうち、任意の
半数の遊星歯車と太陽歯車の噛み合いと、残りの半数の
遊星歯車と太陽歯車の噛み合いとの作用線上の位相差が
正面法線ピッチの1/2となるように各遊星歯車を配置
したことを特徴とする手段とした。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.
また、請求項3記載の低騒音歯車装置では、2軸の歯車
にそれぞれ噛み合う1軸の歯車と3軸の歯車との歯数が
相違する3軸平行歯車装置において、前記1軸の歯車と
2軸の歯車の噛み合い率と、2軸の歯車と3軸の歯車の
噛み合い率とを致させると共に、1軸の歯車と2軸の歯
車の噛み合いと、2軸の歯車と3軸の歯車の噛み合いと
の作用線上の位相差が、正面法線ピッチ1/2となるよ
うに各歯車軸を配置したことを特1¥1とする手段とし
た。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.
また、請求項4記載の低騒音歯車装置では、2軸の歯車
軸に備えた同一歯数の2つの歯車と、それぞれ噛み合う
1軸の歯車と3軸の歯車との歯数が同一である3軸平行
歯車装置において、前記1軸の歯車と2軸の一方の歯車
の噛み合いと、2軸のもう一方の歯車と3軸の歯車の噛
み合いとの作用線上の位相差が正面法線ピッチ1/2と
なるように2軸の両歯車相互の位相をずらせたことを特
徴とする手段とした。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.
また、請求項5記載の低騒音歯車装置では、2軸の歯車
軸に備えた同一歯数の2つの歯車とそれぞれ噛み合う1
軸の歯車と3軸の歯車との歯数が相違する3軸平行歯車
装置において、前記1軸の歯車と2軸の一方の歯車の噛
み合い率と、2軸のもう一方の歯車と3軸の歯車の噛み
合い率とを致させると共に、1軸の歯車と2軸の一方の
歯車の噛み合いと、2軸のもう一方の歯車の噛み合いと
の作用線上の位相差が正面法線ピッチ1/2となるよう
に2軸の両歯車相互の位相をずらせたことを特徴とする
手段とした。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
(作 用)
請求項1記載の低騒音歯車装置では、1軸の歯車と2軸
の歯車との噛み合いによる振動と、2軸の歯車と3軸の
歯車との噛み合いによる振動が生じるが、この振動原因
となる歯のばね剛さの変動周期は正面法線ピッチと対応
するので、1軸の歯車と2軸の歯車の噛み合いと、2軸
の歯車と3軸の歯車の噛み合いとの作用線上の位相差を
正面法線ピッチの1/2とすることにより、振動原因と
なる歯のばね剛さの波形も互いに1/2周期位相のすれ
た関数となり、従って、両振動が互いに打ち消し合うよ
うに逆位相の波形となり、1軸の歯車と3軸の歯車の歯
数が同一である3軸平行歯車装置における装置全体とし
ての歯車騒音が低減化される。(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.
また、請求項2記載の低騒音歯車装置では、偶数個の遊
星歯車のうち任意の半数の遊星歯車と太陽歯車の噛み合
いによる振動と、残り半数の遊星歯車と太陽歯車の噛み
合いによる振動とが互いに打ち消し合うように逆位相の
波形となり遊星歯車装置における装置全体としての歯車
騒音が低減化される。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.
また、請求項3記載の低騒音歯車装置では、1軸の歯車
と2軸の歯車の噛み合い率と、2軸の歯車と3軸の歯車
の噛み合い率とを一致させたことで、1軸の歯車と3軸
の歯車との歯数が相違する3軸平行歯車装置においても
、1軸の歯車と2軸の歯車の噛み合いによる振動と、2
軸の歯車と3軸の歯車の噛み合いによる振動とが互いに
打ち消し合うように逆位相の波形となり、装置全体とし
ての歯車騒音が低減化される。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.
また、請求項4記載の低騒音歯車装置では、2軸の両歯
車相違の位相ずれにより、2軸の歯車に備えた同一歯数
の2つの歯車とそれぞれ噛み合う1軸の歯車と3軸の歯
車との歯数が同一である3軸平行歯車装置においても、
1軸の歯車と2軸の一方の歯車の噛み合いによる振動と
、2軸のもう一方の歯車と3軸の歯・車の噛み合いによ
る振動とが互いに打ち消し合うような逆位相の波形とな
り、装置全体としての歯車騒音が低減化される。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.
また、請求項5記載の低騒音歯車装置では、1軸の歯車
と2軸の一方の歯車の噛み合い率と、2軸のもう一方の
歯車と3軸の歯車の噛み合い率とを一致させたことで、
2軸の歯車軸に備えた同歯数の2つの歯車とそれぞれ噛
み合う1軸の歯車と3軸の歯車との歯数が相違する3軸
平行歯車装置においても、前記第4項発明の場合と同様
に両振動が互いに打ち消し合うような逆位相の波形とな
り、装置全体としての歯車騒音が低減化される。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.
(実施例) 以下、本発明の実施例を図面により詳述する。(Example) Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
まず、第1実施例の構成を説明する。First, the configuration of the first embodiment will be explained.
第1図〜第3図は請求項1記載の発明に対応す。1 to 3 correspond to the invention set forth in claim 1.
る第1実施例の低騒音歯車装置A1を示す説明図であっ
てこの実施例では、2軸のはすは歯車2aにそれぞれ噛
み合う1軸のはすば歯車1aと3軸はすば歯車3aとの
歯数が同一であり、かつ、1軸の歯車軸1bと、2軸の
歯車軸2bと、3軸の歯車軸3bとがそれぞれ平行に配
置された3軸平行歯車装置となっている。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. .
そして、第3図に示すように、1軸のはすげ歯車1aと
2軸のはすげ歯車2aの噛み合い状態を示す同時接触線
4aと、2軸のはすげ歯車2aと3軸のはすば歯車3a
の噛み合い状態を示す同時接触線5aとの同一作用線5
b上での位相差6aが、正面目法線ピッチ(tes)7
aの1/2となるように各歯車軸1b、2b、3bが配
置されている。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.
即ち、3つの歯車軸1b、2b、3bの中心点○l、0
2103のなす角Yが、
Z2:2軸のはすげ歯車2aの歯数
n :整数
となるように各歯車軸1b、2b、3bが配置されてい
る。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.
ここで、δは次式で与えられる。Here, δ is given by the following formula.
V92:2軸のはすば歯車2aの基礎円半径tes :
正面法線ピッチ
尚、第3図中、4bは1軸のはすげ歯車1aと2軸のは
すば歯車2bとの噛み合い作用線、4Cは同噛み合い長
さ、5bは2軸のはすば歯車2日と3軸のはすば歯車3
aとの噛み合い作用線、5Cは同噛み合い長さ、2Cは
2軸のはすば歯車2aの基礎円、2dは同歯先円、1C
は1軸のはすげ歯車1aの基礎円、3Cは3軸のはすげ
歯車3日の基礎円である。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.
次に、作用を説明する。Next, the effect will be explained.
この実施例におけるような3軸平行歯車装置にあっては
、1軸のはすば歯車1aと2軸のはすば歯車2aとの噛
み合いによる振動と、2軸のはすば歯車2aと3軸のは
すげ歯車3aとの噛み合いによる振動が生じる。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.
この振動の原因は、歯車の噛み合いにより移動する歯の
接触点と歯車中心点との間隔の変動に基づく歯のはね剛
さにの変動にあり、この歯のはね剛さKは、第4図に示
すように周期関数をなし、その周期は正面法線ピッチ(
tes)7aと対応する。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.
尚、第4図において8は1軸のはすは歯車1aと2軸の
はすげ歯車2aとのかみ合による歯のはね剛さKの波形
を、また、9は2軸のはすげ歯車2aと3軸のはすは歯
車3日との噛み合いによる歯のはね剛さにの波形を示し
ている。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.
一方、1軸のはすは歯車1aと2軸のはすげ歯車2aと
の噛み合一いと状態を示す同時接触線5日とは、同一作
用線5b上で正面法線ピッチ(tes)7aの1/2の
位相差を持たせているので、前記歯のばね剛さKの波形
8,9も互いに1/2周期付相のずれた関数となる。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.
従って、1軸のはすげ歯車1aと2軸のはすは歯車2a
との噛み合いによる振動と、2軸のはすは歯車2aと3
軸のはすは歯車3aとの噛み合いによる振動とが互いに
打ち消し合うように逆位相の波形となり、歯車装置全体
としての歯車の噛み合い振動(歯車騒音)が低減化され
ることになる。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.
以上説明してきたように、第1実施例の低騒音歯車装置
A1にあっては、1軸のはすは歯車1aと2軸のはすば
歯車2aのかみ合いと、2軸のはすは歯車2aと3軸の
はすげ歯車3aのかみ合いとの作用線上の位相差が、正
面法線ピッチ(tes)7aの1/2となるように各歯
車軸1b、2b、3bを配置した為、1軸のはすは歯車
1aと3軸のはすば歯車3aの歯数か同一である3軸平
行歯車装置において、装置全体としての噛み合い振動(
歯車騒音)を低減化できるようになる。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.
また、上記のように歯車騒音の低減化か各歯車軸ib、
2b、3bの配置を変えるだけで達成できるので部材強
度や動力伝達力に悪影響を及ぼすことはないし、新たな
部材や加工工程の追加によるコストアップを生せしめる
こともない。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.
次に、第2実施例について説明する。Next, a second example will be described.
請求項2gc!載の発明に対応する第2実施例の低騒音
歯車装置A2は、第5図及び第6図に示すように、太陽
歯車10にそれぞれ噛み合う4つの遊星歯車+1.12
.13.14の歯数が全て同である遊星歯車装置、即ち
5軸平行歯車装置となっている。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.
尚、図中15はリンク状内歯車を示し、また、前記各歯
車の種類としては、はすは歯車が用いられている。In the figure, reference numeral 15 indicates a link-shaped internal gear, and each type of gear is a helical gear.
そして、太陽歯車10に対する第1遊星歯車11及び第
3遊星歯車13の噛み合い状態を示す同時接触線16と
、同じく太陽歯車10に対する第2遊星歯車12及び第
4遊星歯車14の噛み合い状態を示す同時接触線17と
の同一作用線12b上での位相差6bが、それぞれ正面
法線ピッチ(tes)7bの1/2となるように各遊星
歯車M、12,13.14が配置されている。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.
即ち、この実施例では、第1遊星歯車11、太陽歯車1
0及び第2′fi星歯車12の中心点0O102のなす
角Y及び第3遊星歯車13、太陽歯車10及び第4遊星
歯車14の中心点○、。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.
0.04のなす角Yとが、前記第1実施例と同様に、
Zs:太陽歯車10の歯数
n :整数
となるように各遊星歯車11’、12,13.14が配
置されている。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. .
ここで、δは次式で与えられる。Here, δ is given by the following formula.
Y9S:太陽歯車10の基礎円半径
tes:正面法線ピッチ
尚、第6図中、+1b、12b、13b、14bは、各
遊星歯車!、12,13.14と太陽歯車10との噛み
合い作用線、10aは太陽歯車10の基礎円、lla、
12a、13a、14aは各遊星歯車の基礎円である。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.
従って、この実施例の低騒音歯車装置A2にあっては、
太陽歯車10に対する第1遊星歯車11及び第3遊星歯
車13の噛み合いによる振動と、太陽歯車10に対する
第2遊星歯車12及び第4遊星は歯車14の噛み合いに
よる振動とが互いに打ち消し合うように逆位相の波形と
なり、遊星歯車装置における歯車の噛み合い振動(歯車
騒音)が低減化されることになる。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.
尚、この実施例における太陽歯車10に対する関係をリ
ング状内歯車15との関係に適用することによって、リ
ング状内歯車15との噛み合いによる振動を低減化する
ことができるが、各遊星歯車11.12,13.14と
の噛み合い率はリング状内歯車15との関係の方が太陽
歯車10との関係の場合よりも大きく、歯のばね剛さの
変動は小さくなるので、太陽歯車10との関係で条件設
定した方が騒音防止効果は高くなる。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.
次に、第3実施例について説明する。Next, a third example will be described.
請求項3記載の発明に対応する第3実施例の低騒音歯車
装置A3は、第7図〜第9図に示すように、2軸のはす
げ歯車2aにそれぞれ噛み合う1軸のはすば歯車1aと
3軸のはすば歯車3aとの歯数が相違すると共に、1軸
の歯車軸1bと、2軸の歯車軸2bと、3軸の歯車軸3
bとがそれぞれ平行に配置された3軸平行歯車装下とな
っている。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.
そしてこの実施例では、1軸のはすば歯車1aと3軸の
はすげ歯車3aとの歯数が相違している関係上、特に1
軸のはすば歯車1aと2軸のはすば歯車2aとの噛み合
い率と、2軸のはすば歯車2aと3軸のはすば歯車3a
との噛み合い率とが正面噛み合い率及び重なり噛み合い
率において共に等しくなるように形成されると共に、1
軸のはすは歯車1aと2軸のはすば歯車2aの噛み合い
状態を示す同時接触線4aと、2軸のはすば歯車2aと
3軸のはすば歯車3aの噛み合い状態を示す同時接触線
5aとの同一作用線5b上での位相差6aが正面法線ピ
ッチ(tes)7cの1/2となるように各歯車軸1b
、2b、3bが配置されている。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.
即ち、3つの歯車軸+b、2b、3bの中心点01・0
2・03のなす角Yが、
Z2:2軸のはすげ歯車2aの歯数
n 、整数
V92:2軸のはすげ歯車2aの基礎円半径tes :
正面法線ピッチ
mo、モジュール
となるように各歯車軸1b、2b、3bが配置される。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.
尚、第9図中、4bは1軸のはすば歯車1aと2軸のは
すは歯車2aとの噛み合い作用線、4Cは同噛み合い長
さ、5bは2軸のはすば歯車2aと3軸のはすば歯車3
aとの噛み合い作用線、5cは同噛み合い長さ、2Cは
2軸のはすげ歯車2aの基礎円、1Cは1軸のはすば歯
車1aの基礎円、3Cは3軸のはすは歯車3aの基礎円
である。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.
従って、この実施例の低騒音歯車装置A3にあっては、
1軸のはすば歯車1aと2軸のはすは歯車2aとの噛み
合い率と、2軸のはすげ歯車2aと3軸のはすは歯車3
aとの噛み合い率とが歯車の噛み合いによる起振動とな
る歯のばね剛さ変動を決定する正面噛み合い率及び重な
り噛み合い率において共に等しくなるように形成した為
、1軸はすば歯車1aと3軸のはすは歯車3aとの歯数
が相違した3軸平行歯車装置においても、1軸のはすげ
歯車1aと2軸のはすば歯車2aとの噛み合いによる振
動と、2軸のはすげ歯車2aと3軸のはすば歯車3aと
の噛み合いによる振動とが互いに打ち消し合うように逆
位相の波形にすることができ、歯車装置全体としての歯
車の噛み合い振動(歯車騒音)を低減化できることにな
る。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.
次に、第4実施例について説明する。Next, a fourth example will be described.
請求項4記叔の発明に対応する第4実施例の低騒音歯車
装置A4は、第10図及び第11図に示すように、2軸
の歯車軸2bに備えた同一歯数の2つのはすば歯車2a
、2eとそれぞれ噛み合う1軸のはすは歯車1aと3軸
のはすば歯車3aとの歯数が同一である3軸平行歯車装
置となっている。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.
そして、この実施例では、各歯車軸1b、2b、3bの
中心点01.Oz、03のなす角度Yが、
である場合において、1軸のはすげ歯車1aと2軸の一
方のはすば歯車2aの噛み合いとのすば歯車a噛み合い
と、2軸のもう一方のはすば歯車2eと3軸のはすば歯
車3aの噛み合いとの同一作用線上での位相差が正面法
線ピッチ(tes)の1/2となるように2軸の両はす
ば歯車2a、2e相互の位相をずらせた状態に設けられ
ている。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.
即ち、第11図に示すように、2軸の一方の歯車2aの
歯形20aともう一方の歯車2eの歯形20eどの位相
差nが、
となるように両歯車2a、2eが配置されている。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.
従って、本実施例においても前記第1実施例の場合と同
様の効果が得られることになる。Therefore, the same effects as in the first embodiment can be obtained in this embodiment as well.
次に、第5実施例について説明する。Next, a fifth example will be described.
請求項5記載の発明に対応する第5実施例の低騒音歯車
装[A5は、第12図にすよう1軸のはすば歯車1aと
3軸のはすば歯車3aの歯数が相違している点以外は、
前記第4実施例の低騒音歯車装置A4と同様の3軸平行
歯車装置となっている。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.
このため、前記第4実施例における条件の他に、1軸の
はすげ歯車1aと2軸の一方のはすげ歯車2aの噛み合
い率と、2軸のもう一方のはすは歯車2eと3軸のはす
げ歯車3aの噛み合い率とを一致させるという条件か付
加されることによって、前記第4実施例の場合と同様の
効果が得られることになる。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.
以上本発明の実施例を図面により詳述してきたが、具体
的な構成はこの実施例に限定されるのもではなく、本発
明の要旨を逸脱しない範囲における設計変更等が合って
も本発明に含まれる。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.
例えば、実施例では、はすは歯車を用いる場合を示した
が、歯車の種類は任意である。For example, in the embodiment, a case where a helical gear is used is shown, but the type of gear may be arbitrary.
(発明の効果)
以上説明してきたように、請求項1記我の低騒音歯車装
置にあっては、1軸の歯車と2軸の歯車の噛み合いと、
2軸の歯車と3軸の歯車のかみ合いとの作用線上の位相
差が、正面法線ピッチ1/2となるように各歯車軸を配
置した為、部材強度や動力伝達に悪影響を及ぼすことな
く、且つ、新たな部材や加工工程の追加によるコストア
ップを生ゼしぬることなしに、2軸の歯車にそれぞれ噛
み合う1軸の歯車と3軸の歯車との歯数が同一である3
細手行歯車装置における振動(歯車騒音)を低減化でき
る。(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.
また、請求項2記載の低騒音歯車装置にあっては、偶数
個の遊星歯車のうち、任意の半数の遊星歯車と太陽歯車
の噛み合いと、残りの半数の遊星歯車と太陽歯車の噛み
合いとの作用線上の位相差が正面法線ピッチの1/2と
なるように各遊星歯車を配置した為、部材強度や動力伝
達に悪影響を及ぼすことなく、且つ、新たな部材や加工
工程の追加によるコストアップを生ゼしぬることなしに
太陽歯車にそれぞれ噛み合う偶数個の遊星歯車を有する
遊星歯車装置における振動(歯車騒音)を低減化できる
。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.
また、請求項3記載の低騒音歯車装置にあっては、1軸
の歯車と2軸の歯車の噛み合い率と、2軸の歯車と3軸
の歯車の噛み合い率とを一致させると共に、1軸の歯車
と2軸の歯車の噛み合いと、2軸の歯車と3軸の歯車の
噛み合いとの作用線上の位相差が、正面法線ピッチ1/
2となるように各歯車軸を配置した為、部材強度や動力
伝達に悪影響を及ぼすことなく、且つ、新たな部材や加
工工程の追加によるコストアップを生ゼしぬることなし
に、2軸の歯車にそれぞれ噛み合う1軸の歯車と3軸の
歯車との歯数が相違する3細手行歯車装置における振動
(歯車騒音)を低減化できる。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.
また、請求項4記載の低騒音歯車装置にあっては、1軸
の歯車と2軸の一方の歯車の噛み合いと、2軸のもう一
方の歯車と3軸の歯車の噛み合いとの作用線上の位相差
が正面法線ピッチ1/2となるように2軸の両歯車相互
の位相をずらせた為、部材強度や動力伝達に悪影響を及
ぼすことなく、且つ、新たな部材や加工工程の追加によ
るコストアップを生ゼしぬることなしに、2軸の歯車軸
に備えた同一歯数の2つの歯車とそれぞれ噛み合う1軸
の歯車と3軸の歯車との歯数が同一である3細手行歯車
装置における振動(歯車騒音)を低減化できる。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.
また、請求項5記載の低騒音歯車装置にあっては、1軸
の歯車と2軸の一方の歯車の噛み合い率と、2軸のもう
一方の歯車と3軸の歯車の噛み合い率とを一致させると
共に、1軸の歯車と2軸の方の歯車の噛み合いと、2軸
のもう一方の歯車の噛み合いとの作用線上の位相差が、
正面法線ピッチ1/2となるように2軸の両歯車相互の
位相をずらせた為、部材強度や動力伝達に悪影響を及ぼ
すことなく、且つ、新たな部材や加工工程の追加による
コストアップを生ゼしぬることなしに、2軸の歯車軸に
備えた同一歯数の2つの歯車とそれぞれ噛み合う1軸の
歯車と3軸の歯車との歯数が相違する3軸並行歯車にお
ける振動(歯車騒音)を低減化できる。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.
第1図は本発明第1実施例の低騒音歯車装置を示す側面
図、第2図は同歯車の全体配置図、第3図は同歯車の噛
み合い状況の詳細を示す説明図、第4図は歯のばね剛さ
の時間変化を示す図、第5図は本発明第2実施例を示す
歯車の全体配置図、第6図は同歯車の噛み合い状況の詳
細を示す説明図、第7図は本発明第3実施例を示す側面
図、第8図は同歯車の全体配置図、第9図は同歯車の噛
み合い状況の詳細を示す説明図、第10図は、本発明第
4実施例を示す側面図、第11図は同歯車の位相ずれ状
態を示す説明図、第12図は本発明第5実施例を示す側
面図、第13図は従来の低騒音歯車装置を示す説明図で
ある。
1ら・・・1軸のはすげ歯車
2a・・・2軸のはすげ歯車
3a・・・3軸のはすば歯車
4b、5b・・・作用線
7a・・・正面法線ピッチ
O・・・太陽歯車
1・・・第1遊星歯車
2・・・第2遊星歯車
3・・・第3遊星歯車
4・・・第4遊星歯車
7b・・・正面法線ピッチ
Mb、+2b、13b、14b・・−作用線時間
第10図
A=
/
/
第12図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)
歯車との歯数が同一である3軸平行歯車装置において、 前記1軸の歯車と2軸の歯車のかみ合いと、2軸の歯車
と3軸の歯車の噛み合いとの作用線上の位相差が、正面
法線ピッチの1/2となるように各歯車軸を配置したこ
とを特徴とする低騒音歯車装置。 2)太陽歯車にそれぞれ噛み合う偶数個の遊星歯車を有
する遊星歯車装置において、 前記偶数個の遊星歯車装置のうち、任意の半数の遊星歯
車と太陽歯車の噛み合いと、残りの半数の遊星歯車と太
陽歯車の噛み合いとの作用線上の位相差が正面法線ピッ
チの1/2となるように各遊星歯車を配置したことを特
徴とする低騒音歯車装置。 3)2軸の歯車にそれぞれ噛み合う1軸の歯車と3軸の
歯車との歯数が相違する3軸平行歯車装置において、 前記1軸の歯車と2軸の歯車の噛み合い率と、2軸の歯
車と3軸の歯車の噛み合い率とを一致させると共に、1
軸の歯車と2軸の歯車の噛み合いと、2軸の歯車と3軸
の歯車の噛み合いとの作用線上の位相差が、正面法線ピ
ッチ1/2となるように各歯車軸を配置したことを特徴
とする低騒音歯車装置。 4)2軸の歯車軸に備えた同一歯数の2つの歯車と、そ
れぞれ噛み合う1軸の歯車と3軸の歯車との歯数が同一
である3軸平行歯車装置において、前記1軸の歯車と2
軸の一方の歯車の噛み合いと、2軸のもう一方の歯車と
3軸の歯車の噛み合いとの作用線上の位相差が正面法線
ピッチ1/2となるように2軸の両歯車相互の位相をず
らせたことを特徴とする低騒音歯車装置。 5)2軸の歯車軸に備えた同一歯数の2つの歯車とそれ
ぞれ噛み合う1軸の歯車と3軸の歯車との歯数が相違す
る3軸平行歯車装置において、前記1軸の歯車と2軸の
一方の歯車の噛み合い率と、2軸のもう一方の歯車と3
軸の歯車の噛み合い率とを一致させると共に、1軸の歯
車と2軸の一方の歯車の噛み合いと、2軸のもう一方の
歯車の噛み合いとの作用線上の位相差が正面法線ピッチ
1/2となるように2軸の両歯車相互の位相をずらせた
ことを特徴とする低騒音歯車装置。[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.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63156360A JPH0826918B2 (en) | 1988-06-24 | 1988-06-24 | Low noise gear device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63156360A JPH0826918B2 (en) | 1988-06-24 | 1988-06-24 | Low noise gear device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH028537A true JPH028537A (en) | 1990-01-12 |
JPH0826918B2 JPH0826918B2 (en) | 1996-03-21 |
Family
ID=15626055
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP63156360A Expired - Lifetime JPH0826918B2 (en) | 1988-06-24 | 1988-06-24 | Low noise gear device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0826918B2 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2010149573A (en) * | 2008-12-24 | 2010-07-08 | Jtekt Corp | Electric power steering device |
JP2010169191A (en) * | 2009-01-22 | 2010-08-05 | Nissan Motor Co Ltd | Triaxial gear device |
US8225690B2 (en) | 2007-02-19 | 2012-07-24 | Toyota Jidosha Kabushiki Kaisha | Power transmission device |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61161463U (en) * | 1985-03-28 | 1986-10-06 |
-
1988
- 1988-06-24 JP JP63156360A patent/JPH0826918B2/en not_active Expired - Lifetime
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61161463U (en) * | 1985-03-28 | 1986-10-06 |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8225690B2 (en) | 2007-02-19 | 2012-07-24 | Toyota Jidosha Kabushiki Kaisha | Power transmission device |
DE102008000337B4 (en) * | 2007-02-19 | 2021-06-24 | Toyota Jidosha Kabushiki Kaisha | Power transmission device |
JP2010149573A (en) * | 2008-12-24 | 2010-07-08 | Jtekt Corp | Electric power steering device |
JP2010169191A (en) * | 2009-01-22 | 2010-08-05 | Nissan Motor Co Ltd | Triaxial gear device |
Also Published As
Publication number | Publication date |
---|---|
JPH0826918B2 (en) | 1996-03-21 |
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