JPH10122310A - Gear device - Google Patents
Gear deviceInfo
- Publication number
- JPH10122310A JPH10122310A JP8270594A JP27059496A JPH10122310A JP H10122310 A JPH10122310 A JP H10122310A JP 8270594 A JP8270594 A JP 8270594A JP 27059496 A JP27059496 A JP 27059496A JP H10122310 A JPH10122310 A JP H10122310A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- lubricating oil
- tooth
- oil
- tooth surface
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0456—Lubrication by injection; Injection nozzles or tubes therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0493—Gearings with spur or bevel gears
- F16H57/0495—Gearings with spur or bevel gears with fixed gear ratio
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は歯車装置に係り、特
に、高速大容量において歯面の焼き付き限界および摩耗
限界を向上させるのに好適な歯車装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear train, and more particularly to a gear train suitable for improving the seizure limit and wear limit of a tooth surface at high speed and large capacity.
【０００２】[0002]
【従来の技術】ピッチ円周速の大きい高速形の歯車装置
においては、歯のかみこみ側から潤滑油を供給すると、
歯の頂、背隙に油を閉じ込めるポンプ仕事や、油を周速
にまで加速する潤滑油加速仕事などの、いわゆる撹拌損
失が大きくなり、歯車装置の効率が低下するばかりでな
く、発熱量の増加による歯面焼き付き限界の低下などの
問題が起きることがある。2. Description of the Related Art In a high-speed gear device having a large pitch circumferential speed, when lubricating oil is supplied from the tooth engaging side,
The so-called agitation loss, such as the pump work to confine the oil in the top of the teeth and the back space and the lubricating oil accelerating work to accelerate the oil to the peripheral speed, increases the efficiency of the gear unit and reduces the amount of heat generated. Problems such as a decrease in the seizure limit due to the increase may occur.
【０００３】低速の歯車装置の場合、歯のかみこみ側か
ら給油したほうが、潤滑、冷却効果が高いことは経験的
に知られていたが、高速歯車装置においては、上述した
理由により、反かみこみ側からの給油が一般的であっ
た。この場合、反かみこみ側からの給油の主たる目的
は、歯面の冷却であり、歯面の潤滑は歯に付着した潤滑
油、およびかみこみ側から吸入される油霧のみで行な
う。ところが、このような方法では、かみあい歯面に十
分な潤滑油が供給されず、特に、歯幅中央部から後半の
かみあい終わり部の近傍では、歯面潤滑のための油が不
足して高温となり、高速大容量の歯車装置においては、
焼き付きや摩耗などといった歯面損傷を引き起こすとい
う問題があった。[0003] It has been empirically known that in the case of a low-speed gear device, lubrication and cooling effects are higher when lubrication is performed from the tooth meshing side. Refueling from the side was common. In this case, the main purpose of oil supply from the counter-engaging side is to cool the tooth surface, and lubrication of the tooth surface is performed only by the lubricating oil attached to the teeth and the oil mist sucked from the meshing side. However, in such a method, sufficient lubricating oil is not supplied to the meshing tooth surface. In high-speed, large-capacity gear units,
There has been a problem of causing tooth surface damage such as seizure and wear.
【０００４】歯車装置においては、大小歯車の熱容量比
は半径の二乗に比例して大きくなる。したがって、歯面
や軸受における発熱量が大きい高速大容量の歯車装置で
は、大小歯車間に大きな温度差が生じ、熱膨張による歯
の相対的なピッチ差が増加して、歯の荷重分担が不正と
なり、はすば歯車では歯の片当たりが生じる。例えば、
Ｍａａｇ Ｇｅａｒ Ｂｏｏｋ Ｐ.１８９〜１９１に
示されるように、熱膨張により小歯車の歯のピッチは大
歯車よりも大きくなり、減速かみあいではかみあい終わ
り部、増速かみあいではかみあい始め部の歯が片当たり
となる。大容量の歯車装置は、一般に歯幅が大きく片当
たりの影響が大きいため、歯を十分に潤滑、冷却しなけ
れば、かみあい歯面の焼き付きや摩耗などを招き、歯車
装置の寿命を著しく縮める。In a gear device, the heat capacity ratio of the large and small gears increases in proportion to the square of the radius. Therefore, in a high-speed and large-capacity gear device that generates a large amount of heat on the tooth surfaces and bearings, a large temperature difference occurs between the large and small gears, and the relative pitch difference between the teeth due to thermal expansion increases, and the tooth load sharing is incorrect. In the helical gear, a tooth contact occurs. For example,
As shown in Mag Gear Book pages 189 to 191, the pitch of the teeth of the small gear is larger than that of the large gear due to thermal expansion. Becomes Since a large-capacity gear device generally has a large tooth width and a large influence on a single contact, if the teeth are not sufficiently lubricated and cooled, seizure or wear of the meshing tooth surface is caused, and the life of the gear device is significantly shortened.
【０００５】このような大小歯車間に生じる温度差を解
消するには、例えば、特公平４−１７１３４８号公報記
載のウォーム歯車減速機に示されるように、小歯車を潤
滑油面下に配設するとともに、小歯車の遠心力を利用し
て、軸端に設けた油取り入れ穴から油を吸入し、小歯車
軸と同心に設けた流路を通過させた後、歯車軸表面に設
けた排油穴より油を排出することにより、小歯車を外部
および内部の両側から冷却するという方法がある。これ
は歯面の摩擦による発熱量の特に大きなウォーム歯車減
速機において、非常に有効な方法である。また、トポロ
ジカル研削盤などを用いて、熱変形後に歯当たりが最適
になるように歯面を３次元的に整形し、歯の片当たりを
防止している例もある。In order to eliminate such a temperature difference between the large and small gears, for example, as shown in a worm gear reducer described in Japanese Patent Publication No. 4-171348, a small gear is arranged below the lubricating oil level. At the same time, the centrifugal force of the small gear is used to suck oil from an oil intake hole provided at the shaft end, and to pass through a flow path provided concentrically with the small gear shaft. There is a method in which the small gear is cooled from both the outside and the inside by discharging the oil from the oil hole. This is a very effective method for a worm gear reducer that generates a large amount of heat due to friction of the tooth surface. Further, there is also an example in which a tooth surface is three-dimensionally shaped by using a topological grinder or the like so as to optimize the tooth contact after thermal deformation, thereby preventing the tooth contact.
【０００６】[0006]
【発明が解決しようとする課題】しかし、前述のウォー
ム歯車減速機のような構造では、小歯車軸全体を潤滑油
面下に配設しなければならず、油の撹拌損失が大きくな
るため、高速形の歯車装置には適用することができな
い。また、トポロジカル研削を行なうには、高価な専用
研削盤が必要であり、加工コストが大きくなる。However, in a structure such as the worm gear reducer described above, the entire small gear shaft must be disposed below the lubricating oil level, and the oil agitation loss increases. It cannot be applied to high-speed gear units. In addition, an expensive dedicated grinding machine is required to perform the topological grinding, and the processing cost is increased.
【０００７】本発明の目的は、油の撹拌損失が小さく、
歯面の焼き付き限界および摩耗限界の高い歯車装置を安
価に提供することにある。An object of the present invention is to reduce oil agitation loss,
An object of the present invention is to provide an inexpensive gear device having a high seizure limit and a high wear limit of the tooth surface.
【０００８】[0008]
【課題を解決するための手段】本発明では前記の課題
を、以下のように解決する。請求項１記載発明は、少な
くとも１対の歯車を有する歯車装置において、前記歯車
の反かみこみ側に設けた潤滑油供給管以外に、かみこみ
側の歯幅中央部から後半に潤滑油を供給する潤滑油供給
管を設けたことを特徴とする。これにより、油の撹拌損
失による発熱をあまり増加させずに、特に高温となる歯
幅中央部から後半のかみあい終わり部の歯面を、よく潤
滑して冷却し、歯面の焼き付き限界および摩耗限界を向
上させることができる。請求項２記載発明は、少なくと
も１対の歯車を有する歯車装置において、前記歯車の反
かみこみ側に設けた潤滑油供給管以外に、かみこみ側の
歯幅中央部から後半に油霧を供給する噴霧管を設けたこ
とを特徴とする。油霧すなわちオイルミストを、かみこ
み側の所定の部位に供給することにより、歯面の潤滑冷
却効果が向上する。請求項３記載発明は、少なくとも１
対の歯車を有する歯車装置において、前記歯車を収納す
る歯車箱内壁と、前記内壁に配設されたリブおよび歯車
の外周で構成される空間の断面積が、前記歯車の回転方
向に沿って次第に小さくなり、歯のかみこみ側の歯幅中
央部から後半で最小となるように、前記内壁およびリブ
を構成したことを特徴とする。これにより、歯車箱内壁
とリブと歯車外周とで囲まれた空間が、空気流路として
歯車外周に沿って、回転方向に次第に断面積が小さくな
るため、空気の流速が早くなり、特に高温となるかみあ
い終わり部を効率よく冷却することになる。また、請求
項４記載発明は、前記歯の反かみこみ側に設けた潤滑油
供給管以外に、歯車周上に潤滑油を供給する潤滑油供給
管を、少なくとも１本以上設けたことを特徴とするの
で、歯車周上に供給された潤滑油は、空気流とともに霧
状になって高速で流れ、特に高温となるかみあい終わり
部を効率よく潤滑および冷却し、焼き付きや摩耗などと
いった歯面損傷を防止する。また、請求項５記載発明
は、前記歯車は円筒歯車であることを特徴とし、特に、
はすば歯車や、やまば歯車などに好適に適用できる。ま
た、請求項６記載発明は、前記歯車のピッチ円周速が、
９０ｍ／ｓ以上であることを特徴とする。特に、高速大
容量の歯車装置において、歯面を冷却するとともに、少
量の潤滑油、あるいは油霧をかみこみ側の所定の部位に
供給することにより、油の撹拌損失による発熱をあまり
増加させずにかみあい歯面を効率よく潤滑および冷却で
きる。According to the present invention, the above-mentioned problems are solved as follows. According to a first aspect of the present invention, in a gear device having at least one pair of gears, lubricating oil is supplied to a latter half from a central portion of a tooth width on a biting side in addition to a lubricating oil supply pipe provided on a counterbiting side of the gear. The lubricating oil supply pipe is provided. As a result, the heat generated by the loss of oil agitation does not increase so much, and the tooth surfaces from the center of the tooth width, which is at a high temperature, to the end of the last half of the meshing are well lubricated and cooled. Can be improved. According to a second aspect of the present invention, in the gear device having at least one pair of gears, an oil mist is supplied to the latter half from the central portion of the tooth width on the biting side in addition to the lubricating oil supply pipe provided on the counterbiting side of the gear. A spray tube is provided. By supplying the oil mist, that is, the oil mist, to a predetermined portion on the biting side, the lubrication and cooling effect of the tooth surface is improved. The invention according to claim 3 includes at least one
In a gear device having a pair of gears, a cross-sectional area of a space formed by an inner wall of a gear box housing the gears and a rib disposed on the inner wall and an outer periphery of the gears gradually increases along a rotation direction of the gears. The inner wall and the rib are configured to be smaller and to be minimum in the latter half from the central portion of the tooth width on the tooth engagement side. As a result, the space surrounded by the inner wall of the gear box, the ribs, and the outer periphery of the gear is gradually reduced in cross-sectional area in the rotational direction along the outer periphery of the gear as an air flow path, so that the flow velocity of the air is increased, and particularly at high temperatures. The end of the meshing will be efficiently cooled. Further, the invention according to claim 4 is characterized in that at least one or more lubricating oil supply pipes for supplying lubricating oil on the circumference of the gear are provided in addition to the lubricating oil supply pipe provided on the counter-biting side of the teeth. As a result, the lubricating oil supplied on the circumference of the gears is atomized with the air flow and flows at a high speed.Efficiently lubricates and cools the meshing end, which is particularly hot, and reduces tooth surface damage such as seizure and wear. To prevent The invention according to claim 5 is characterized in that the gear is a cylindrical gear.
It can be suitably applied to helical gears, helical gears, and the like. In the invention according to claim 6, the pitch circumferential speed of the gear is:
It is at least 90 m / s. Particularly, in a high-speed and large-capacity gear device, by cooling a tooth surface and supplying a small amount of lubricating oil or oil mist to a predetermined portion on the biting side, heat generation due to oil agitation loss is not significantly increased. The meshing tooth surface can be efficiently lubricated and cooled.
【０００９】[0009]
【発明の実施の形態】以下、本発明の実施の形態を、図
面を参照して説明する。 （実施形態１）本発明による歯車装置の第１の実施形態
を図１に示す。図１（ａ）は上面図、図１（ｂ）は軸方
向の正面図である。本実施形態は、発電機用の高速平行
軸はすば歯車装置に対する発明の適用例であって、図に
示すように、小歯車１および大歯車２は、歯車軸３およ
び４と一体、あるいは嵌合されて成り、歯車軸は軸受５
によって回転自在に保持されている。歯車装置で使用さ
れる潤滑油は、いったん油槽１２に蓄えられ、オイルポ
ンプ１３から、ろ過器１４、クーラ１５を経て、軸受５
および歯面給油配管１８Ａ、１８Ｂに供給される。歯面
給油のための潤滑油は、歯面給油配管１８Ａから潤滑油
供給管７Ａを通り、歯の反かみこみ側に配設した潤滑油
供給ノズル８Ａより、かみあい部１６に供給されるが、
これとは別に、歯面給油配管１８Ｂから潤滑油供給管７
Ｂを通り、歯のかみこみ側の歯幅中央部から後半の任意
の位置に設置した、潤滑油供給ノズル８Ｂにまで到る潤
滑油流路を設け、潤滑油をかみこみ側のかみあい終わり
部、すなわち歯幅中央部から後半の任意の歯面へ供給す
るようになっている。Embodiments of the present invention will be described below with reference to the drawings. (Embodiment 1) FIG. 1 shows a first embodiment of a gear device according to the present invention. FIG. 1A is a top view, and FIG. 1B is an axial front view. This embodiment is an application example of the invention to a high-speed parallel shaft helical gear device for a generator, and as shown in the figure, a small gear 1 and a large gear 2 are integrated with gear shafts 3 and 4, or The gear shaft is a bearing 5
It is rotatably held by. The lubricating oil used in the gear device is temporarily stored in an oil tank 12, and is passed from an oil pump 13 through a filter 14 and a cooler 15 to a bearing 5.
And to the tooth surface oil supply pipes 18A, 18B. The lubricating oil for lubricating the tooth surface is supplied from the lubricating oil supply pipe 18A to the meshing portion 16 through the lubricating oil supply pipe 7A, and from the lubricating oil supply nozzle 8A disposed on the opposite side of the teeth.
Apart from this, the lubricating oil supply pipe 7
B, a lubricating oil flow path extending from the central portion of the tooth width on the tooth intrusion side to the lubricating oil supply nozzle 8B is provided at an arbitrary position in the latter half. That is, it is supplied from the central portion of the tooth width to an arbitrary tooth surface in the latter half.
【００１０】反かみこみ側から潤滑油を供給する場合、
かみあい歯面を潤滑するのは歯面に付着している油と、
かみこみ側から吸入される油霧のみとなる。そのため負
荷歯面上に存在する潤滑油が不足し、かみあい終わり部
近傍では負荷歯面上の潤滑油温度が上昇し、歯面が冷却
されない。したがって、かみあい歯面における摩擦発熱
量が大きい大容量の歯車装置においては、焼き付きや摩
耗などといった歯面損傷を引き起こす可能性がある。減
速歯車の場合は前述した歯の熱変形によるかみあい終わ
り部の片当たりがあるため、この傾向はさらに助長され
る。一方、かみこみ側から給油することにより、負荷歯
面上の潤滑油量を増加させることができるが、例えば、
ピッチ円周速９０ｍ／ｓを超えるような高速形の歯車装
置においては、撹拌損失が大きくなるため歯車全体を冷
却するのに十分な油量を供給することができない。When lubricating oil is supplied from the anti-biting side,
The lubrication of the meshing tooth surface depends on the oil adhering to the tooth surface,
Only the oil mist sucked in from the biting side. Therefore, the lubricating oil existing on the load tooth surface is insufficient, and the lubricating oil temperature on the load tooth surface increases near the end of the meshing, so that the tooth surface is not cooled. Therefore, in a large-capacity gear device that generates a large amount of frictional heat on the meshing tooth surface, tooth surface damage such as seizure and wear may be caused. In the case of a reduction gear, this tendency is further promoted because there is one end of the meshing end due to the thermal deformation of the teeth described above. On the other hand, by lubricating from the biting side, the amount of lubricating oil on the load tooth surface can be increased.
In a high-speed gear device having a pitch circumferential speed exceeding 90 m / s, an agitation loss becomes large, so that an oil amount sufficient to cool the entire gear cannot be supplied.
【００１１】そこで図中に示すように、歯の反かみこみ
側に配設した潤滑油供給ノズル８Ａから、歯車全体を冷
却するのに十分な油量をかみあい歯面に供給するととも
に、かみこみ側に設けた潤滑油供給ノズル８Ｂから、歯
のかみこみ側かみあい終わり部に潤滑油を局所的に供給
することにより、特に高温となるかみあい終わり部近傍
の負荷歯面を効果的に潤滑および冷却し、焼き付きや摩
耗などといった歯面損傷を防止する。供給される潤滑油
は歯車本体と比べて十分低温なため、少量でも歯の冷却
効果が高い。また、潤滑油は歯幅全域にわたって油を供
給する場合に比べて短時間で反かみこみ側から排出さ
れ、供給量自体も少ないため油の撹拌損失は小さい。Therefore, as shown in the figure, a lubricating oil supply nozzle 8A disposed on the opposite side of the tooth is provided with a sufficient amount of oil for cooling the entire gear to the meshing tooth surface, and at the same time, meshing. By locally supplying lubricating oil from the lubricating oil supply nozzle 8B provided on the side of the meshing end of the tooth meshing side, the load tooth surface in the vicinity of the meshing end where the temperature becomes high is effectively lubricated and cooled. To prevent tooth surface damage such as burn-in and wear. Since the supplied lubricating oil is sufficiently lower in temperature than the gear body, even a small amount of the lubricating oil has a high tooth cooling effect. Further, the lubricating oil is discharged from the reentrant side in a shorter time than in the case where the oil is supplied over the entire tooth width, and the supply amount itself is small, so that the oil stirring loss is small.
【００１２】（実施形態２）本発明による歯車装置の第
２の実施形態を図２に示す。図２（ａ）は上面図、図２
（ｂ）は軸方向の正面図である。なお、符号の１、２、
３、４、５、７Ａ、８Ａ、１２、１３、１４、１５、１
８Ａ、１８Ｂで示す構成要素は、実施形態１と共通であ
り、ここでは説明を省略する。(Embodiment 2) FIG. 2 shows a second embodiment of the gear device according to the present invention. FIG. 2A is a top view, and FIG.
(B) is a front view in the axial direction. It should be noted that reference numerals 1, 2,
3, 4, 5, 7A, 8A, 12, 13, 14, 15, 1
The components indicated by 8A and 18B are common to the first embodiment, and the description is omitted here.
【００１３】本実施形態では、歯の反かみこみ側に配設
され、歯面に潤滑油を供給する潤滑油供給管７Ａ以外
に、かみこみ側かみあい終わり部に、少なくとも１個以
上の潤滑油噴霧管７Ｃを、歯すじに沿って配設する。エ
ア源１７からの圧縮空気は、ろ過器１４を通り、噴霧管
７Ｃ内で潤滑油と混合され油霧（オイルミスト）とな
る。この油霧を、かみこみ側の歯幅中央部から後半の任
意の歯面に、潤滑油噴霧ノズル８Ｃから供給する。In this embodiment, at least one lubricating oil is provided at the end of meshing side engagement, in addition to the lubricating oil supply pipe 7A provided on the anti-meshing side of the tooth and supplying lubricating oil to the tooth surface. The spray pipe 7C is arranged along the tooth trace. The compressed air from the air source 17 passes through the filter 14 and is mixed with the lubricating oil in the spray pipe 7C to form an oil mist. This oil mist is supplied from the lubricating oil spray nozzle 8C to an arbitrary tooth surface in the latter half from the center of the tooth width on the biting side.
【００１４】歯の反かみこみ側に配設した潤滑油供給ノ
ズル８Ａから、歯車全体を冷却するのに十分な油量をか
みあい歯面に供給するとともに、かみこみ側かみあい終
わり部に、局所的に油霧を供給することにより、特に高
温となるかみあい終わり部近傍の負荷歯面を効果的に潤
滑し、焼き付きや摩耗などといった歯面損傷を防止す
る。かみこみ側から供給される油霧は、大部分が粘性の
極めて小さい空気であるから、油霧による撹拌損失の増
加は小さい。歯車周速がさらに大きくなる場合は、噴霧
管７Ｃからの油霧供給量を増やすことにより、潤滑油の
撹拌損失をあまり増加させずに潤滑能力をさらに高める
ことができる。A sufficient amount of oil for cooling the entire gear is supplied to the meshing tooth surface from a lubricating oil supply nozzle 8A disposed on the non-meshing side of the tooth. By supplying oil mist to the surface, the load tooth surface, especially near the end of the meshing where the temperature becomes high, is effectively lubricated, and the tooth surface damage such as seizure or wear is prevented. Most of the oil mist supplied from the biting side is air with extremely low viscosity, and therefore, the increase in the stirring loss due to the oil mist is small. When the gear peripheral speed is further increased, the lubricating ability can be further increased without increasing the stirring loss of the lubricating oil by increasing the supply amount of the oil mist from the spray pipe 7C.
【００１５】（実施形態３）本発明による歯車装置の第
３の実施形態を図３に示す。図３（ａ）は上面図、図３
（ｂ）は軸方向の正面図である。なお、符号の１、２、
３、４、５、７Ａ、８Ａで示す構成要素は、実施形態１
と共通であり、ここでは説明を省略する。(Embodiment 3) FIG. 3 shows a third embodiment of the gear device according to the present invention. FIG. 3A is a top view, and FIG.
(B) is a front view in the axial direction. It should be noted that reference numerals 1, 2,
Components indicated by 3, 4, 5, 7A and 8A are the same as those in the first embodiment.
The description is omitted here.
【００１６】本実施形態では、歯車箱上ケース６Ａの内
壁を、歯車１および２の外周に沿って形成し、この上ケ
ースの内壁に、上ケース補強用のリブ１９Ａ、１９Ｂ、
１９Ｃ、１９Ｄおよび１９Ｅを設ける。リブ１９Ａと１
９Ｂは、歯車箱上下ケースの大歯車側合わせ面９Ａ近傍
を起点にして、大歯車外周に沿って配設され、リブ１９
Ｃと１９Ｄは、上下ケースの小歯車側合わせ面９Ｂ近傍
を起点にして、小歯車外周に沿って配設される。リブ１
９Ａと１９Ｂ、および１９Ｃと１９Ｄの間隔は歯車の回
転方向に沿って次第に小さくなり、歯のかみこみ側かみ
あい終わり部１０近傍において最小となる。また、この
位置で、リブ１９Ａと１９Ｃ、および１９Ｂと１９Ｄの
終端部をそれぞれ結合し、歯幅方向にリブ１９Ｅを設け
て、このリブにより、リブ１９Ａ−１９Ｃと１９Ｂ−１
９Ｄとを接続する。In this embodiment, the inner wall of the gear box upper case 6A is formed along the outer circumference of the gears 1 and 2, and the upper case inner walls are provided with upper case reinforcing ribs 19A, 19B,
19C, 19D and 19E are provided. Ribs 19A and 1
9B is disposed along the outer periphery of the large gear starting from the vicinity of the large gear side mating surface 9A of the upper and lower cases of the gear box.
C and 19D are disposed along the outer periphery of the small gear starting from the vicinity of the small gear side mating surface 9B of the upper and lower cases. Rib 1
The distance between 9A and 19B and between 19C and 19D becomes gradually smaller along the rotation direction of the gear, and becomes minimum near the meshing end portion 10 of the tooth on the meshing side. At this position, the end portions of the ribs 19A and 19C and the end portions of the ribs 19B and 19D are connected, and a rib 19E is provided in the face width direction. The ribs 19A-19C and 19B-1
9D.
【００１７】以上のように、歯車箱上ケース内壁のリブ
１９Ａ、１９Ｂ、１９Ｃ、１９Ｄ、１９Ｅを構成するこ
とにより、歯車箱上ケース内壁とリブ、および歯車の外
周とで囲まれた空間が、空気の流路として歯車の外周に
沿って形成され、歯車が回転することにより、この流路
を歯車箱内の空気が高速で流れることになる。これによ
り、歯車箱中に充満する油霧を効率よく集めて歯面へと
供給することができる。空気の流路は、歯車の外周に沿
って回転方向に次第に断面積が小さくなるため、歯車の
外周に沿って流れる気流の流速は、さらに大きくなる。
また、リブ１９Ｅにより、気流はかみあい部へと方向を
変える。この結果、歯のかみこみ側かみあい終わり部
へ、油滴を含んだ気流が高速で流れ込み、特に高温とな
るかみあい終わり部を効率よく潤滑および冷却し、焼き
付きや摩耗などといった歯面損傷を防止する。As described above, by forming the ribs 19A, 19B, 19C, 19D, and 19E of the inner wall of the gear box upper case, the space surrounded by the inner wall of the gear box upper case, the ribs, and the outer periphery of the gear can be formed. An air flow path is formed along the outer periphery of the gear, and the rotation of the gear causes air in the gear box to flow at a high speed through this flow path. Thereby, the oil mist filling the gear box can be efficiently collected and supplied to the tooth surface. Since the cross-sectional area of the air flow path gradually decreases in the rotation direction along the outer periphery of the gear, the flow velocity of the airflow flowing along the outer periphery of the gear further increases.
Further, the rib 19E changes the direction of the airflow to the meshing portion. As a result, the air flow including the oil droplets flows into the meshing end portion of the tooth at the high speed, and efficiently lubricates and cools particularly the meshing end portion that becomes high in temperature, thereby preventing tooth surface damage such as seizure and wear.
【００１８】歯のかみこみ側へ供給される油滴を含んだ
気流の速度は、歯車周速に近く、空気の粘性が小さいこ
とと合わせて、撹拌損失は非常に小さい。また、歯車箱
の上ケース補強用リブは、歯車箱の剛性確保のために必
要なものであり、本方法はその配置を変更するだけで実
現できるので、製造コストの増加が極めて少ない。さら
に、歯車周速が大きいほど歯面の潤滑および冷却効果が
高まるため、本方法は高速歯車装置に好適である。The speed of the air flow containing the oil droplets supplied to the tooth biting side is close to the peripheral speed of the gear, and together with the low viscosity of the air, the stirring loss is very small. Further, the upper case reinforcing ribs of the gear box are necessary for securing the rigidity of the gear box, and the present method can be realized only by changing the arrangement thereof, so that an increase in manufacturing cost is extremely small. Furthermore, since the lubrication and cooling effects of the tooth surface increase as the gear peripheral speed increases, the present method is suitable for a high-speed gear device.
【００１９】本実施形態では、大小の歯車双方に空気の
流路を設けているが、歯車箱上ケースの形状変更および
リブ配置の変更により、この流路をどちらか片側のみに
設けてもよい。また、リブの起点を、歯車箱上下ケース
合わせ面近傍から、歯のかみこみ側にずらせてリブ長を
短くしてもよいし、同様の働きをするカバーを歯車外周
に設けることにより、歯車箱上ケースの設計の自由度を
高めることもできる。In this embodiment, the air flow path is provided on both the large and small gears. However, this flow path may be provided on only one side by changing the shape of the upper case of the gear box and changing the rib arrangement. . Further, the starting point of the rib may be shifted from the vicinity of the gear box upper / lower case mating surface to the tooth engagement side to shorten the rib length, or a cover having the same function may be provided on the outer periphery of the gear box, so that the upper surface of the gear box is provided. The degree of freedom in case design can also be increased.
【００２０】さらに図に示すように、潤滑油供給管１１
を小歯車の空気流路上に設け、少量の潤滑油を小歯車歯
面に供給してもよい。歯面に供給された潤滑油は衝突の
衝撃で飛散し、油滴となって歯のかみこみ側へと運ばれ
るため、直接かみこみ側へ給油するよりも撹拌損失は小
さい。本方法によれば、潤滑油供給管からの潤滑油供給
量を変更することにより、歯のかみこみ側へ供給される
空気と油滴の混合比を容易に変更できる。例えば、歯車
周速が同一で伝達動力がより大きい歯車装置の場合、歯
の潤滑および冷却性能をさらに高くする必要があるが、
本方法によれば供給空気と油滴の混合比を変更すること
により、これを実現できる。Further, as shown in FIG.
May be provided on the air passage of the small gear, and a small amount of lubricating oil may be supplied to the tooth surface of the small gear. The lubricating oil supplied to the tooth surface is scattered by the impact of the collision and is carried as oil droplets to the biting side of the tooth. Therefore, the agitation loss is smaller than when the oil is directly supplied to the biting side. According to this method, by changing the amount of lubricating oil supplied from the lubricating oil supply pipe, it is possible to easily change the mixing ratio of the air and the oil droplets supplied to the bite side of the teeth. For example, in the case of a gear device having the same gear peripheral speed and larger transmission power, it is necessary to further improve the lubrication and cooling performance of the teeth,
According to the present method, this can be realized by changing the mixing ratio between the supply air and the oil droplets.
【００２１】本実施形態では、潤滑油供給管１１を小歯
車の空気流路上に設けているが、これは大歯車の空気流
路上、あるいは大小の歯車双方に設けてもよい。また、
流路の入り口近傍に設けることもできる。また、上述の
各実施形態は、円筒歯車で説明しているが、かさ歯車な
どに対しても、同様に、本発明を適用することができ
る。In the present embodiment, the lubricating oil supply pipe 11 is provided on the air flow path of the small gear, but it may be provided on the air flow path of the large gear or both the large and small gears. Also,
It can also be provided near the entrance of the flow channel. In each of the embodiments described above, the cylindrical gear is described. However, the present invention can be similarly applied to a bevel gear and the like.
【００２２】[0022]
【発明の効果】本発明によれば、油の撹拌損失をあまり
増加させることなく、特に高温となる歯のかみあい終わ
り部を局所的に潤滑および冷却でき、もって歯面の焼き
付き限界および摩耗限界を向上させることができる。According to the present invention, it is possible to locally lubricate and cool the meshing end portion of a tooth which becomes high in temperature without significantly increasing the oil agitation loss, thereby reducing the seizure limit and wear limit of the tooth surface. Can be improved.
【図１】本発明の第１の実施形態を示す上面図および正
面図である。FIG. 1 is a top view and a front view showing a first embodiment of the present invention.
【図２】本発明の第２の実施形態を示す上面図および正
面図である。FIG. 2 is a top view and a front view showing a second embodiment of the present invention.
【図３】本発明の第３の実施形態を示す上面図および正
面図である。FIG. 3 is a top view and a front view showing a third embodiment of the present invention.
１ 小歯車 ２ 大歯車 ３ 小歯車軸 ４ 大歯車軸 ５ 軸受 ６Ａ 歯車箱上ケース ６Ｂ 歯車箱下ケース ７Ａ 反かみこみ側潤滑油供給管 ７Ｂ かみこみ側潤滑油供給管 ７Ｃ 油霧供給管 ８Ａ、８Ｂ 潤滑油供給ノズル ８Ｃ 潤滑油噴霧ノズル ９Ａ、９Ｂ 歯車箱上下ケース合わせ面 １０ 歯の高温部 １１ 空気流路用潤滑油供給管 １２ 油槽 １３ オイルポンプ １４ ろ過器 １５ クーラ １６ 歯車かみあい部 １７ エア源 １８Ａ、１８Ｂ 歯面給油配管 １９Ａ、１９Ｂ、１９Ｃ、１９Ｄ、１９Ｅ 歯車箱上ケ
ース補強用リブReference Signs List 1 small gear 2 large gear 3 small gear shaft 4 large gear shaft 5 bearing 6A gear box upper case 6B gear box lower case 7A counter-engaging lubricating oil supply pipe 7B meshing-side lubricating oil supply pipe 7C oil mist supply pipe 8A 8B Lubricating oil supply nozzle 8C Lubricating oil spray nozzle 9A, 9B Gear box upper and lower case mating surface 10 High temperature part of teeth 11 Lubricating oil supply pipe for air flow path 12 Oil tank 13 Oil pump 14 Filter 15 Cooler 16 Gear meshing part 17 Air source 18A, 18B Tooth-surface lubrication piping 19A, 19B, 19C, 19D, 19E Rib for reinforcing gear box upper case
───────────────────────────────────────────────────── フロントページの続き (72)発明者 阿片 寛志 茨城県土浦市神立町603番地 株式会社日 立製作所土浦工場内 ──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Hiroshi Agata 603, Kandamachi, Tsuchiura-shi, Ibaraki Pref.
Claims (6)
において、前記歯車の反かみこみ側に設けた潤滑油供給
管以外に、かみこみ側の歯幅中央部から後半に潤滑油を
供給する潤滑油供給管を設けたことを特徴とする歯車装
置。1. A gear device having at least one pair of gears, wherein lubrication oil for supplying lubricating oil to a latter half from a central portion of a tooth width on a biting side in addition to a lubricating oil supply pipe provided on a counterbiting side of the gear. A gear device provided with an oil supply pipe.
において、前記歯車の反かみこみ側に設けた潤滑油供給
管以外に、かみこみ側の歯幅中央部から後半に油霧を供
給する噴霧管を設けたことを特徴とする歯車装置。2. A gear device having at least one pair of gears, wherein, in addition to a lubricating oil supply pipe provided on a counter-engaging side of the gear, a spray for supplying oil mist to a latter half from a central portion of the tooth width on the meshing side. A gear device comprising a pipe.
において、前記歯車を収納する歯車箱内壁と、前記内壁
に配設されたリブおよび歯車の外周で構成される空間の
断面積が、前記歯車の回転方向に沿って次第に小さくな
り、歯のかみこみ側の歯幅中央部から後半で最小となる
ように、前記内壁およびリブを構成したことを特徴とす
る歯車装置。3. A gear device having at least one pair of gears, wherein a cross-sectional area of a space formed by an inner wall of a gear box that houses the gears, a rib provided on the inner wall, and an outer periphery of the gears is a gear. Wherein the inner wall and the rib are configured so as to be gradually reduced along the rotation direction of the tooth and to become minimum in the latter half from the central portion of the tooth width on the tooth-entry side.
記歯の反かみこみ側に設けた潤滑油供給管以外に、歯車
周上に潤滑油を供給する潤滑油供給管を、少なくとも１
本以上設けたことを特徴とする歯車装置。4. The gear device according to claim 3, wherein at least one lubricating oil supply pipe for supplying lubricating oil on the circumference of the gear is provided, in addition to the lubricating oil supply pipe provided on the counter-engaging side of the teeth.
A gear device characterized by comprising at least one.
の歯車装置において、前記歯車は円筒歯車であることを
特徴とする歯車装置。5. The gear device according to claim 1, wherein the gear is a cylindrical gear.
の歯車装置において、前記歯車のピッチ円周速が、９０
ｍ／ｓ以上であることを特徴とする歯車装置。6. The gear device according to claim 1, wherein a pitch circumferential speed of the gear is 90%.
m / s or more.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8270594A JPH10122310A (en) | 1996-10-14 | 1996-10-14 | Gear device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8270594A JPH10122310A (en) | 1996-10-14 | 1996-10-14 | Gear device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH10122310A true JPH10122310A (en) | 1998-05-15 |
Family
ID=17488287
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8270594A Pending JPH10122310A (en) | 1996-10-14 | 1996-10-14 | Gear device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH10122310A (en) |
Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11351361A (en) * | 1998-06-09 | 1999-12-24 | Toshiba Mach Co Ltd | Lubricating device and lubricating method for gear device |
| EP1016808A2 (en) | 1998-12-28 | 2000-07-05 | Nissan Motor Company, Limited | Forced-feed lubricating system for gears |
| JP2002340152A (en) * | 2001-05-22 | 2002-11-27 | Nissan Motor Co Ltd | Lubricating device for gear |
| JP2005090270A (en) * | 2003-09-12 | 2005-04-07 | Toyota Motor Corp | Variable compression ratio internal combustion engine |
| JP2005325925A (en) * | 2004-05-14 | 2005-11-24 | Toyota Motor Corp | Lubricating device of gear mechanism |
| WO2009084259A1 (en) * | 2007-12-27 | 2009-07-09 | Aisin Aw Co., Ltd. | Gear rotation transmitting device |
| JP2009281498A (en) * | 2008-05-22 | 2009-12-03 | Isuzu Motors Ltd | Lubricating device of transmission |
| CN101985974A (en) * | 2010-11-12 | 2011-03-16 | 洛阳舒诚机械设备有限公司 | Cooling lubrication system and method for pile driver reducer |
| JP2012219962A (en) * | 2011-04-12 | 2012-11-12 | Toyota Motor Corp | Gear lubrication device |
| CN104070697A (en) * | 2014-06-18 | 2014-10-01 | 韦啟武 | Motor speed changing box structure for oil press |
| JP2018025284A (en) * | 2016-08-12 | 2018-02-15 | トヨタ自動車株式会社 | Lubrication device of gear device for vehicle |
| CN108799473A (en) * | 2018-08-31 | 2018-11-13 | 沃德传动（天津）股份有限公司 | A kind of speed reducer lubrication calandria structure |
| CN109519525A (en) * | 2018-12-25 | 2019-03-26 | 盐城博尔福机电科技发展有限公司 | The connection structure of governor governor gear and fixing axle |
| EP3663615A1 (en) * | 2018-12-04 | 2020-06-10 | AVL MTC Motortestcenter AB | Gearbox |
| WO2021121246A1 (en) * | 2019-12-18 | 2021-06-24 | 长城汽车股份有限公司 | Decelerator and vehicle |
| CN115679568A (en) * | 2022-11-21 | 2023-02-03 | 南通新佳机电有限公司 | Composite multi-needle machine head of quilting and embroidering machine |
| CN116438948A (en) * | 2023-04-22 | 2023-07-18 | 青岛郁金香机械有限公司 | Power-driven harrow |
-
1996
- 1996-10-14 JP JP8270594A patent/JPH10122310A/en active Pending
Cited By (24)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11351361A (en) * | 1998-06-09 | 1999-12-24 | Toshiba Mach Co Ltd | Lubricating device and lubricating method for gear device |
| EP1016808A2 (en) | 1998-12-28 | 2000-07-05 | Nissan Motor Company, Limited | Forced-feed lubricating system for gears |
| JP2002340152A (en) * | 2001-05-22 | 2002-11-27 | Nissan Motor Co Ltd | Lubricating device for gear |
| JP2005090270A (en) * | 2003-09-12 | 2005-04-07 | Toyota Motor Corp | Variable compression ratio internal combustion engine |
| JP2005325925A (en) * | 2004-05-14 | 2005-11-24 | Toyota Motor Corp | Lubricating device of gear mechanism |
| JP4665434B2 (en) * | 2004-05-14 | 2011-04-06 | トヨタ自動車株式会社 | Lubricator for gear mechanism |
| WO2009084259A1 (en) * | 2007-12-27 | 2009-07-09 | Aisin Aw Co., Ltd. | Gear rotation transmitting device |
| DE112008002342T5 (en) | 2007-12-27 | 2010-07-15 | Aisin Aw Co., Ltd. | Gear wheel turning device |
| JP2009281498A (en) * | 2008-05-22 | 2009-12-03 | Isuzu Motors Ltd | Lubricating device of transmission |
| CN101985974A (en) * | 2010-11-12 | 2011-03-16 | 洛阳舒诚机械设备有限公司 | Cooling lubrication system and method for pile driver reducer |
| JP2012219962A (en) * | 2011-04-12 | 2012-11-12 | Toyota Motor Corp | Gear lubrication device |
| CN104070697A (en) * | 2014-06-18 | 2014-10-01 | 韦啟武 | Motor speed changing box structure for oil press |
| JP2018025284A (en) * | 2016-08-12 | 2018-02-15 | トヨタ自動車株式会社 | Lubrication device of gear device for vehicle |
| CN107725743A (en) * | 2016-08-12 | 2018-02-23 | 丰田自动车株式会社 | Lubricating arrangement for the gear apparatus of vehicle |
| US10539224B2 (en) | 2016-08-12 | 2020-01-21 | Toyota Jidosha Kabushiki Kaisha | Lubricating device of gear apparatus for vehicle |
| CN108799473A (en) * | 2018-08-31 | 2018-11-13 | 沃德传动（天津）股份有限公司 | A kind of speed reducer lubrication calandria structure |
| EP3663615A1 (en) * | 2018-12-04 | 2020-06-10 | AVL MTC Motortestcenter AB | Gearbox |
| CN109519525A (en) * | 2018-12-25 | 2019-03-26 | 盐城博尔福机电科技发展有限公司 | The connection structure of governor governor gear and fixing axle |
| CN109519525B (en) * | 2018-12-25 | 2024-01-30 | 盐城博尔福机电科技发展有限公司 | Connection structure of speed regulating gear and fixed shaft of speed regulator |
| WO2021121246A1 (en) * | 2019-12-18 | 2021-06-24 | 长城汽车股份有限公司 | Decelerator and vehicle |
| CN115679568A (en) * | 2022-11-21 | 2023-02-03 | 南通新佳机电有限公司 | Composite multi-needle machine head of quilting and embroidering machine |
| CN115679568B (en) * | 2022-11-21 | 2023-10-03 | 南通新佳机电有限公司 | Compound multi-needle handpiece of quilting embroidery machine |
| CN116438948A (en) * | 2023-04-22 | 2023-07-18 | 青岛郁金香机械有限公司 | Power-driven harrow |
| CN116438948B (en) * | 2023-04-22 | 2024-01-26 | 青岛郁金香机械有限公司 | Power-driven harrow |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH10122310A (en) | Gear device | |
| JP5265592B2 (en) | Gear train lubricator | |
| JP7030249B2 (en) | Front bearing oil lubrication mechanism and motor drive assembly of water-cooled motor | |
| JP4958889B2 (en) | Gear train lubricator | |
| WO2009084259A1 (en) | Gear rotation transmitting device | |
| JP3937754B2 (en) | Gear lubricator | |
| US20040094364A1 (en) | Lubrication system for high speed planet gears | |
| JP2009180371A (en) | Gear device for rail vehicle | |
| CN106574619B (en) | Convolute-hydrodynamic mechanics and its maintaining method | |
| DE102006003213A1 (en) | Lubricating oil supplying device, has hollow shaft, within which ladling device is arranged, which protrudes into oil ring rotating in operation of rotary hollow shaft | |
| JP2000508744A (en) | Transmission lubrication device | |
| JP3925145B2 (en) | Bearing lubrication structure of rotating shaft | |
| JP4869513B2 (en) | Lubricator for transmission | |
| JP2010139002A (en) | Gear device for rail vehicle | |
| CN209705250U (en) | A kind of water-cooled machine fore bearing oil lubrication mechanism and motor driven assembly | |
| US7465158B2 (en) | Reduction gear pump | |
| JP2007028700A (en) | Rotary electric machine | |
| JPH0741128U (en) | Lubrication mechanism of power transmission device | |
| JPH0960712A (en) | Gear device | |
| CN110822067A (en) | Auxiliary lubricating structure of transmission device and speed reducer | |
| JP6834863B2 (en) | Bearing lubrication structure | |
| KR970005788B1 (en) | Device for supplying manual transmission with lubricating oil | |
| JPH0633246Y2 (en) | Lubricant induction device for transfer | |
| JPH02176193A (en) | Bearing oiling device for oil-free screw vacuum pump | |
| JPH08383Y2 (en) | Oil lubrication system for gears in spinning machines |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Year of fee payment: 6 Free format text: PAYMENT UNTIL: 20080510 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090510 Year of fee payment: 7 |
|
| LAPS | Cancellation because of no payment of annual fees |