JPH0560204A - Stepped intermediate gear - Google Patents
Stepped intermediate gearInfo
- Publication number
- JPH0560204A JPH0560204A JP24037391A JP24037391A JPH0560204A JP H0560204 A JPH0560204 A JP H0560204A JP 24037391 A JP24037391 A JP 24037391A JP 24037391 A JP24037391 A JP 24037391A JP H0560204 A JPH0560204 A JP H0560204A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- thrust
- stepped intermediate
- thrust force
- teeth
- 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.)
- Pending
Links
Landscapes
- Gears, Cams (AREA)
Abstract
Description
【0001】[0001]
【産業上の利用分野】本考案は、はすば歯車に関してお
り、特に固定した同軸上に段付で2枚のはすば歯車を有
し、該2枚の歯車のスラスト力を相殺させた段付中間歯
車及び回転自在で軸方向移動自在に軸承された回転軸に
固定され歯車ボス部でスラスト力を担持する段付中間歯
車(以下、何れも単に段付中間歯車と称する)に関する
ものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a helical gear, and in particular, has a fixed coaxial two stepped helical gears to cancel the thrust force of the two gears. The present invention relates to a stepped intermediate gear and a stepped intermediate gear (hereinafter, simply referred to as a stepped intermediate gear) that is fixed to a rotating shaft that is rotatably and movably in an axial direction and bears a thrust force at a gear boss portion. is there.
【0002】[0002]
【従来の技術】従来、はすば歯車の段付中間歯車はあら
ゆる方面で多岐にわたり使用されている。はすば歯車に
はスラスト力が作用するため、軸受と歯車ボス部端面に
発生する摩擦力によるトルク損失などの問題を引き起こ
す。そのため、はすば歯車の段付中間歯車の場合、歯す
じのねじれ方向を同方向にし、前段の歯車から駆動力を
受ける駆動側の歯車のスラスト力と該駆動側の歯車から
駆動力を受ける同軸の被動側の歯車のスラスト力とを逆
方向にして、段付中間歯車全体に作用するスラスト力を
低減することが知られている。2. Description of the Related Art Conventionally, stepped intermediate gears of helical gears have been widely used in various fields. Since the thrust force acts on the helical gear, it causes problems such as torque loss due to frictional force generated between the bearing and the end surface of the gear boss. Therefore, in the case of the stepped intermediate gear of the helical gear, the helical directions of the teeth are set in the same direction, and the thrust force of the drive side gear that receives the drive force from the preceding stage gear and the drive force from the drive side gear are received. It is known to reverse the thrust force of the coaxial gear on the driven side to reduce the thrust force acting on the entire stepped intermediate gear.
【0003】[0003]
【発明が解決しようとする課題】しかしながら上記従来
例では、段付中間歯車の各はすば歯車のねじれ方向を同
一にすることは念頭にあるものの該段付中間歯車とかみ
合い前後段の歯車の歯車諸元との関係が前提とされてし
まうことが通常であり、はすば歯車のねじれ角をスラス
ト力の均衡を保つ数値とするように考慮に入れて段付中
間歯車を定めることはしていない。However, in the above-mentioned conventional example, although it is conceived that the helical directions of the helical gears of the stepped intermediate gear are the same, the gears of the front and rear stages meshing with the stepped intermediate gear are not considered. It is usually assumed that the relationship with the gear specifications is assumed, and it is not necessary to determine the stepped intermediate gear by taking into consideration the helical gear twist angle so that the thrust force is balanced. Not not.
【0004】又、歯車製作上の点から例えばねじれ角を
15°とする場合があり、必ずしもねじれ角が限定され
ない歯切機械を用いる場合も段付中間歯車の大小2枚の
歯車を同ねじれ角例えば15°とすることも多い。この
ため、段付中間歯車に生ずるスラスト力は充分に相殺さ
れない。そのため段付中間歯車のボス部と軸受間に加わ
るスラスト力により摩擦損失が発生してトルク損失が生
じ、又軸受とボス部の摩耗を生ぜしめて耐久性を損ず
る。From the point of view of gear manufacturing, for example, the twist angle may be 15 °, and when a gear cutting machine whose twist angle is not necessarily limited is used, two large and small stepped intermediate gears have the same twist angle. For example, it is often set at 15 °. Therefore, the thrust force generated in the stepped intermediate gear is not sufficiently offset. Therefore, the thrust force applied between the boss portion of the stepped intermediate gear and the bearing causes friction loss and torque loss, and wear of the bearing and the boss portion causes wear to impair durability.
【0005】本発明は、固設した軸に回転自在又は回転
自在で軸方向移動自在に支持された回転軸に固定された
段付中間歯車において、作用するスラスト力がほぼ完全
に相殺される段付中間歯車を提供することを目的とす
る。According to the present invention, in a stepped intermediate gear fixed to a rotating shaft rotatably supported by a fixed shaft or rotatably supported so as to be movable in the axial direction, a thrust force acting on the stepped intermediate gear is almost completely offset. It is intended to provide an attached intermediate gear.
【0006】[0006]
【課題を解決するための手段】本発明は同軸上に、動力
源側の歯車と噛み合う駆動側の歯車と、該駆動側の歯車
から駆動力を受け負荷側の歯車と噛み合う被動側の歯車
とを軸方向移動自在に支持されたはすばの段付中間歯車
において、駆動側の歯車の歯数、モジュール、ねじれ角
をそれぞれ、z1 ,m1,β1 、被動側の歯車の歯数、
モジュール、ねじれ角をそれぞれz2 ,m2 ,β2 とす
ると、 であり、かつ歯すじのねじれ方向が同方向であることを
特徴とする段付中間歯車である。SUMMARY OF THE INVENTION According to the present invention, a driving-side gear that coaxially meshes with a power-source-side gear and a driven-side gear that receives a driving force from the driving-side gear and meshes with a load-side gear. In the stepped intermediate gear of the helical shaft supported movably in the axial direction, the number of teeth of the drive side gear, the module, and the helix angle are respectively z 1 , m 1 , β 1 , and the number of teeth of the driven side gear. ,
If the module and twist angle are z 2 , m 2 and β 2 , respectively, In addition, the stepped intermediate gear is characterized in that the twisting directions of the tooth lines are the same.
【0007】はすば段付中間歯車の駆動側歯車の歯数、
モジュール、ねじれ角、ピッチ円半径、切線荷重、スラ
スト力をそれぞれz1 ,m1 ,β1 ,r1 ,Tt1,Fx1
、被動側歯車の歯数、モジュール、ねじれ角、ピッチ
円半径、切線荷重、スラスト力をそれぞれ、z2 ,m
2 ,β2 ,r2 ,Ft2,Fx2とすれば、段付中間歯車の
駆動側と被動側とに生じるトルクTは T=Ft1r1 =Ft2r2 よって、 また、 Fx1=Ft1tanβ1 Fx2=Ft2tanβ2 駆動側被動側の歯車のスラスト力を相殺させるためには
歯のねじれ方向を同一方向とし、且つ Fx1=Fx2 Ft1tanβ1 =Ft2tanβ2 ・・・・・・(2) 式(1) ÷(2) とすると つまり、はすば段付中間歯車のスラスト力を相殺させる
には、ねじれ角の方向を同方向にして、 を満足するようにすればよい。The number of teeth of the drive side gear of the helical stepped intermediate gear,
Module, helix angle, pitch radius, cutting line load, thrust force z 1 , m 1 , β 1 , r 1 , T t1 , F x1 respectively
, Number of teeth of driven side gear, module, helix angle, pitch radius, cutting line load, thrust force, respectively z 2 , m
2 , β 2 , r 2 , F t2 , and F x2 , the torque T generated on the driving side and the driven side of the stepped intermediate gear is T = F t1 r 1 = F t2 r 2 Further, F x1 = F t1 tanβ 1 F x2 = F t2 tanβ 2 In order to cancel the thrust force of the gear on the driving side and the driven side, the twisting directions of the teeth should be the same direction, and F x1 = F x2 F t1 tanβ 1 = F t2 tan β 2 ········· (2) Equation (1) ÷ (2) That is, in order to cancel the thrust force of the helical stepped intermediate gear, the directions of the torsion angles should be the same, Should be satisfied.
【0008】実際には、歯面や軸での摩擦によるトルク
損失があるため、 Ft1r1 ≦Ft2r2 である。また、トルク損失を含む駆動側のトルクの大き
さはモジュールの大きさ、軸の径、摩擦係数の値、駆動
側と被動側の噛み合い位置の関係などによって計算によ
って求められるが、負荷のトルクの大きさによつて異な
るため、大雑把には、 Ft1r1 ≒Ft2r2 として、 としても、かなりのトルク損失の低減に寄与できる。ま
た、このとき、はすば段付中間歯車全体に作用するスラ
スト力Fx は、 Fx =|Fx1−Fx2|=|Ft1tanβ1 −Ft2tanβ2 |≧0 であるが、Fx は負荷のトルクの大きさによって当然そ
の大きさは異なるが、若干の大きさであれば、トルク損
失をさほど大きくすることなく、段付中間歯車全体にス
ラスト荷重が作用する。一般に、固定軸に回転自在に備
えられている段付中間歯車或は軸方向移動自在に軸承さ
れた回転軸に固定された段付中間歯車は、円滑に回転さ
せるために、スラスト方向に対して、多少移動できるよ
うに歯車ボス部とスラスト軸受面間にすきまを持たせて
ある。仮に、歯車に作用するスラスト力が0であるとす
ると、歯車はスラスト方向の位置が定まらないことにな
る。はすば歯車の場合、重なり噛み合い率を整数にする
ことにより、動力源であるモータのトルク変動が少なく
なるという効果があることは、本発明人が先に提案して
いる。歯車のスラスト方向の位置が変動すると、噛み合
い歯幅が変動し、結果として重なり噛み合い率が変動
し、トルク変動を引き起こしてしまう。その他、歯車の
強度、たわみなどを考察しても、噛み合い歯幅が変動す
ることは好ましくない。本発明によれば、歯車全体に若
干のスラスト力が作用するために、歯車のスラスト方向
の位置が定まり、噛み合い歯幅が安定する。In reality, since there is a torque loss due to friction on the tooth surface and the shaft, F t1 r 1 ≤ F t2 r 2 . In addition, the magnitude of the torque on the drive side including the torque loss is calculated by the size of the module, the diameter of the shaft, the value of the friction coefficient, the relationship between the meshing positions of the drive side and the driven side, etc. Since it depends on the size, roughly, F t1 r 1 ≈ F t2 r 2 Even so, it can contribute to a considerable reduction in torque loss. At this time, the thrust force F x acting on the entire helical stepped intermediate gear is F x = | F x1 −F x2 | = | F t1 tanβ 1 −F t2 tanβ 2 | ≧ 0, The magnitude of F x naturally varies depending on the magnitude of the torque of the load, but if it is a little magnitude, the thrust load acts on the entire stepped intermediate gear without significantly increasing the torque loss. Generally, a stepped intermediate gear that is rotatably provided on a fixed shaft or a stepped intermediate gear that is fixed on a rotating shaft that is axially movably supported, is designed to smoothly rotate in the thrust direction. , There is a gap between the gear boss and the thrust bearing surface so that it can move a little. If the thrust force acting on the gear is zero, the position of the gear in the thrust direction will not be determined. In the case of a helical gear, the present inventor has previously proposed that the effect of reducing the torque fluctuation of the motor that is the power source is reduced by setting the overlapping meshing ratio to an integer. When the position of the gear in the thrust direction changes, the meshing tooth width changes, and as a result, the overlapping meshing ratio changes, causing torque fluctuations. In addition, considering the strength and deflection of the gear, it is not preferable that the meshing tooth width varies. According to the present invention, since a slight thrust force acts on the entire gear, the position of the gear in the thrust direction is determined and the meshing tooth width is stabilized.
【0009】[0009]
「実施例1」はすば歯車の段付中間歯車において、駆動
側の歯車の歯数、モジュール、ねじれ角をそれぞれ、z
1 ,m1 ,β1 、被動側の歯車の歯数、モジュール、ね
じれ角をそれぞれ、z2 ,m2 ,β2 とし、駆動側の歯
車と被動側の歯車のスラスト力をほぼ等しくするには であり、かつ、ねじれ角の方向が同方向であればよい。
例えば、z1 =17,m1=0.6 ,z2 =34,m2=0.4
とすれば、 例えば、β1 =15°のとき、β2 =20.187°とすれば
よい。[Example 1] In the stepped intermediate gear of the helical gear, the number of teeth, the module, and the helix angle of the drive-side gear are respectively z
1 , m 1 and β 1 , the number of teeth of the gear on the driven side, the module, and the twist angle are z 2 , m 2 , and β 2 , respectively, so that the thrust forces of the driving-side gear and the driven-side gear are almost equal. Is And the directions of the twist angles should be the same.
For example, z 1 = 17, m 1 = 0.6, z 2 = 34, m 2 = 0.4
given that, For example, when β 1 = 15 °, β 2 = 20.187 ° may be set.
【0010】図1は、このはすばの段付中間歯車を示し
た図であり、負荷側の不図示の歯車と噛み合う被動側の
歯車1は、z1 =17,m1 =0.6 ,β1 =15°であ
る。動力源側の不図示の歯車と噛み合い、被動側の歯車
1へ駆動力を伝える駆動側の歯車2はz2 =34,m2
=0.4 ,β2 =20.187°である。ねじれ角の方向はこの
場合は歯車1、歯車2とも右であるが、歯車1、歯車2
とも左であってもよい。このようにすれば、歯面や軸受
部での摩擦によるトルク損失がないと仮定すれば、歯車
1と歯車2に作用するスラスト力は等しくなるため、歯
車全体に作用するスラスト力の総和は0となり、スラス
ト方向の摩擦によるトルク損失をなくすことができる。FIG. 1 is a diagram showing a stepped intermediate gear of this helical type. The gear 1 on the driven side that meshes with a gear (not shown) on the load side is z 1 = 17, m 1 = 0.6, β. 1 = 15 °. The gear 2 on the driving side that meshes with a gear (not shown) on the power source side and transmits the driving force to the gear 1 on the driven side is z 2 = 34, m 2.
= 0.4 and β 2 = 20.187 °. In this case, the direction of the twist angle is right for both gear 1 and gear 2, but gear 1 and gear 2
Both may be on the left. In this way, assuming that there is no torque loss due to friction on the tooth flanks or bearings, the thrust forces acting on the gear 1 and gear 2 are equal, so the total thrust force acting on the entire gear is 0. Therefore, torque loss due to friction in the thrust direction can be eliminated.
【0011】実際には、歯面や軸受部での摩擦によるト
ルク損失があるため、この段付中間歯車には、スラスト
荷重が作用する。In reality, since there is a torque loss due to friction on the tooth surface and the bearing portion, a thrust load acts on this stepped intermediate gear.
【0012】例えば、歯車1に作用する切線荷重Ft1を
1kgfとすると、トルク損失がないと仮定すれば、歯
車2に作用する切線荷重Ft2は、 より、Ft2=0.73kgfであるが、実際には、トルク損
失があるため、例えば、Ft2=0.8 kgfであるとする
と Fx1=Ft1tanβ1 =268gf Fx2=Ft2tanβ2 =294gf である。つまり段付中間歯車全体には、Fx =|Fx1−
Fx2|=26gfのスラスト力が作用し、結果として、
段付中間歯車はスラスト方向の位置が定まることにな
る。For example, assuming that the cutting line load F t1 acting on the gear 1 is 1 kgf, assuming that there is no torque loss, the cutting line load F t2 acting on the gear 2 is Therefore, F t2 = 0.73 kgf, but in reality, there is a torque loss. For example, if F t2 = 0.8 kgf, then F x1 = F t1 tan β 1 = 268 gf F x2 = F t2 tan β 2 = 294 gf Is. That is, for the entire stepped intermediate gear, F x = | F x1 −
A thrust force of F x2 | = 26 gf acts, and as a result,
The position of the stepped intermediate gear is determined in the thrust direction.
【0013】仮に、β1 =β2 =20.187°とし、トルク
損失がないとすれば、 より、Ft2=0.75kgf Fx1=Ft1tanβ1 =368gf Fx2=Ft2tanβ2 =276gf である。つまり歯車全体には、Fx =|Fx1−Fx2|=
92gfのスラスト力が作用する。(実際にはトルク損
失がある。)本実施例で示した歯車の諸元の数値はあく
までも1例であり、本発明を限定するものではないこと
は当然である。If β 1 = β 2 = 20.187 ° and there is no torque loss, Therefore, F t2 = 0.75 kgf F x1 = F t1 tan β 1 = 368 gf F x2 = F t2 tan β 2 = 276 gf. That is, the entire gear, F x = | F x1 -F x2 | =
A thrust force of 92 gf acts. (Actually, there is a torque loss.) The numerical values of the specifications of the gears shown in the present embodiment are merely examples, and it goes without saying that the present invention is not limited to these.
【0014】図2は前述の段付中間歯車を有する歯車列
の1実施例である。歯車2は動力源であるモータMのモ
ータ軸と一体である歯車3と噛み合い、歯車1は遊び歯
車4と噛み合い、遊び歯車4は遊び歯車5と、遊び歯車
5は負荷を生ずる回転体Tと一体である歯車6と噛み合
っている。このような歯車列はトルク損失が少なくな
り、モータなどの動力源の最大許容トルクを低減でき、
低消費電力、装置全体の小型化などに寄与する。また、
負荷は何であっても構わない。FIG. 2 shows an embodiment of a gear train having the aforementioned stepped intermediate gear. The gear 2 meshes with a gear 3 that is integral with a motor shaft of a motor M that is a power source, the gear 1 meshes with an idle gear 4, the idle gear 4 is an idle gear 5, and the idle gear 5 is a rotating body T that produces a load. It meshes with an integral gear 6. Such a gear train has less torque loss and can reduce the maximum allowable torque of a power source such as a motor.
It contributes to low power consumption and miniaturization of the entire device. Also,
The load does not matter.
【0015】[0015]
【発明の効果】以上説明したように、はすばの段付中間
歯車において、駆動側の歯車の歯数、モジュール、ねじ
れ角をそれぞれ、z1 ,m1 β1 、被動側の歯車の歯
数、モジュール、ねじれ角をそれぞれ、z2 ,m2 ,β
2 とすると であり、かつ、ねじれ角の方向を同方向とすることによ
り、はすばの段付中間歯車に発生するスラスト力の総和
をほぼ完全に相殺でき、トルク損失の低減が可能とな
る。また、実際には、歯面や軸受部での摩擦によるトル
ク損失があるため、段付中間歯車全体には、若干のスラ
スト方向の力が作用し、スラスト方向の位置が定まる。
このことにより、噛み合い歯幅を安定させることができ
る。As described above, in the stepped intermediate gear of the helical gear, the number of teeth of the gear on the driving side, the module, and the twist angle are respectively z 1 , m 1 β 1 , and the teeth of the gear on the driven side. The number, module, and twist angle are z 2 , m 2 , and β, respectively.
If 2 By making the directions of the torsion angles the same, the total sum of thrust forces generated in the stepped intermediate gear of the helical can be almost completely offset, and the torque loss can be reduced. Further, in reality, since there is torque loss due to friction on the tooth surface and the bearing portion, a slight thrust direction force acts on the entire stepped intermediate gear, and the thrust direction position is determined.
As a result, the meshing tooth width can be stabilized.
【図1】本発明の実施例の平面図である。FIG. 1 is a plan view of an embodiment of the present invention.
【図2】駆動伝達装置の1実施例のフローシートであ
る。FIG. 2 is a flow sheet of one embodiment of a drive transmission device.
1 負荷側の歯車と噛み合う駆動側歯車 2 動力源側の歯車と噛み合う被動側歯車 1 Drive side gear that meshes with the load side gear 2 Driven side gear that meshes with the power source side gear
Claims (1)
動側の歯車と、該駆動側の歯車から駆動力を受け負荷側
の歯車と噛み合う被駆動側の歯車とを軸方向移動自在に
支持されたはすばの段付中間歯車において、駆動側の歯
車の歯数、モジュール、ねじれ角をそれぞれ、z1 ,m
1 ,β1 、被動側の歯車の歯数、モジュール、ねじれ角
をそれぞれz2 ,m2 ,β2 とすると、 であり、かつ歯すじのねじれ方向が同方向であることを
特徴とする段付中間歯車。1. A drive-side gear that meshes with a power-source-side gear and a driven-side gear that receives a driving force from the drive-side gear and meshes with a load-side gear are axially movable coaxially. In the supported stepped intermediate helical gear, the number of teeth, the module and the helix angle of the drive side gear are respectively z 1 , m
1 , β 1 , the number of teeth of the gear on the driven side, the module, and the twist angle are z 2 , m 2 , and β 2 , respectively, The stepped intermediate gear is characterized in that the helical directions of the teeth are the same.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP24037391A JPH0560204A (en) | 1991-08-27 | 1991-08-27 | Stepped intermediate gear |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP24037391A JPH0560204A (en) | 1991-08-27 | 1991-08-27 | Stepped intermediate gear |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH0560204A true JPH0560204A (en) | 1993-03-09 |
Family
ID=17058530
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP24037391A Pending JPH0560204A (en) | 1991-08-27 | 1991-08-27 | Stepped intermediate gear |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0560204A (en) |
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JP2009197976A (en) * | 2008-02-25 | 2009-09-03 | Jtekt Corp | Gear and differential system for vehicle having the same |
US20110237384A1 (en) * | 2010-03-29 | 2011-09-29 | Shimano Inc. | Planetary gear mechanism for a bicycle internal hub transmission |
US11169465B2 (en) | 2019-12-27 | 2021-11-09 | Brother Kogyo Kab Ushiki Kaisha | Image forming apparatus including input element, output element and transmission element for transmitting driving force of motor to roller |
-
1991
- 1991-08-27 JP JP24037391A patent/JPH0560204A/en active Pending
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0783314A (en) * | 1993-09-20 | 1995-03-28 | Canon Inc | Drive gear |
JP2009197976A (en) * | 2008-02-25 | 2009-09-03 | Jtekt Corp | Gear and differential system for vehicle having the same |
US20110237384A1 (en) * | 2010-03-29 | 2011-09-29 | Shimano Inc. | Planetary gear mechanism for a bicycle internal hub transmission |
US8357071B2 (en) * | 2010-03-29 | 2013-01-22 | Shimano Inc. | Planetary gear mechanism for a bicycle internal hub transmission |
TWI453145B (en) * | 2010-03-29 | 2014-09-21 | Shimano Kk | Planetary gear mechanism for a bicycle internal hub transmission |
DE102011001632B4 (en) * | 2010-03-29 | 2015-10-08 | Shimano Inc. | Planetary gear for a hub gear hub |
US11169465B2 (en) | 2019-12-27 | 2021-11-09 | Brother Kogyo Kab Ushiki Kaisha | Image forming apparatus including input element, output element and transmission element for transmitting driving force of motor to roller |
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