WO2004020876A1 - Gear - Google Patents

Gear Download PDF

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Publication number
WO2004020876A1
WO2004020876A1 PCT/JP2003/011024 JP0311024W WO2004020876A1 WO 2004020876 A1 WO2004020876 A1 WO 2004020876A1 JP 0311024 W JP0311024 W JP 0311024W WO 2004020876 A1 WO2004020876 A1 WO 2004020876A1
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WO
WIPO (PCT)
Prior art keywords
tooth
groove
lubricating oil
gear
width
Prior art date
Application number
PCT/JP2003/011024
Other languages
French (fr)
Japanese (ja)
Inventor
Teisuke Bushimata
Eiju Chiba
Minoru Hibino
Original Assignee
Chiba Dies Co., Ltd.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Chiba Dies Co., Ltd. filed Critical Chiba Dies Co., Ltd.
Publication of WO2004020876A1 publication Critical patent/WO2004020876A1/en

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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
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • F16H57/0431—Means for guiding lubricant directly onto a tooth surface or to foot areas of a gear, e.g. by holes or grooves in a tooth flank
    • 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

Definitions

  • the present invention relates to a relatively small gear having a lubricating structure and having relative slippage between teeth.
  • gear forming materials such as metal materials, synthetic resin materials, rubber materials, and metal-synthetic resin composite materials.
  • lubricating oil is effective for suppressing the noise and temperature rise and increasing the durability of all materials.
  • a lubricating oil injection mechanism that injects lubricating oil to the gear tooth surface is provided close to the gear.
  • the gear itself is provided with a lubricating structure for preventing the lubricating oil from running out on the tooth surfaces of the gear contained in the gear box filled with the lubricating oil.
  • This conventional gear is provided with a groove partially cut out from the end of the tooth width near the pitch circle of the tooth surface.
  • the lubricating oil matching the lubricating oil stored in the groove is brought into contact with the lubricating oil, so that the lubricating oil is supplied to the tooth surface in a timely manner, thereby preventing the lubricating oil from running out on the tooth surface. Also, by providing the groove only in a part of the tooth width, the continuity of the connection is prevented from being impaired.
  • the grooves are located near the pitch circle of the tooth surface that receives the stress of the rolling friction, which reduces the strength of the teeth. There is a problem. Further, since the grooves are provided only in a part of the tooth width, there is a problem that the supply of the lubricating oil to the tooth surface becomes uneven. Also, since the groove is located in the middle of the mating effective surface (contact surface between the tooth surfaces), the groove conversely removes lubricating oil from the tooth surface when sliding friction occurs on the tooth surface. There is a problem. Disclosure of the invention
  • the present invention has been made in consideration of the above-described problems, and can effectively supply lubricating oil evenly to the tooth surface without lowering the strength of the teeth while maintaining the continuity of the connection.
  • a technical problem is to provide a gear having a lubricating structure.
  • the groove is formed at an apical end of a mating effective surface of the tooth surface. It is configured as a gear that is characterized by being located in the vicinity of the entire width of the tooth width.
  • the lubricating oil stored in the groove located at the end of the tooth apart from the pitch circle of the tooth surface is extruded in a continuous manner and the relative sliding of the tooth surfaces is caused by the contact surface pressure and the mutual tooth surface.
  • the grooves are provided over the entire width of the teeth, there is no uneven supply of lubricating oil to the tooth surfaces.
  • the groove is located near the end of the tooth flank on the mating effective surface, and lubricating oil is supplied so as to be applied to the tooth flank by the relative sliding of the tooth flank and the contact surface pressure. Therefore, lubricating oil is effectively supplied to the tooth surface.
  • a gear provided with a groove for storing lubricating oil on a tooth surface, wherein the groove is formed on the tooth root side of the effective surface of the tooth surface.
  • the gear is characterized in that it is located near the end of the gear and is disposed over the entire width of the tooth width.
  • the lubricating oil accumulated in the groove located on the root side away from the pitch circle of the tooth surface is extruded in a continuous manner, and the mutual lubrication of the tooth surface and the contact surface pressure cause the mutual lubrication. Supplied so as to apply to the entire width of the face.
  • the groove is located near the end of the tooth surface on the root side of the mating effective surface and is located away from the pitch circle of the tooth surface, the continuity of the mating is maintained and the tooth strength is maintained. Does not decrease.
  • the grooves are provided over the entire width of the teeth, there is no uneven supply of lubricating oil to the tooth surfaces.
  • the groove is located near the root end of the mating effective surface of the tooth surface, and lubricating oil is supplied so as to be applied to each tooth surface by the relative sliding of the tooth surface and the contact surface pressure. However, lubricating oil is effectively supplied to the tooth surface.
  • the lubricating oil is stored in multiple rows.
  • the amount of lubricating oil stored in multiple rows It decreases sequentially toward.
  • the grooves are arranged in a band shape as minute recesses scattered over the entire width of the tooth width. It is configured as a gear that is characterized by
  • the lubricating oil is scattered and stored over the entire tooth width.
  • the recess of the groove is such that the amount of lubricating oil accumulated in the pitch circle gradually decreases. It is configured as a gear characterized by being formed.
  • the amount of lubricating oil that is accumulated as scattered points gradually decreases toward the pitch circle.
  • the forming material is different and the tooth of the effective surface of the tooth surface is different.
  • the gear is characterized by having elasticity to slightly deform the groove located near the end on the rear side.
  • FIG. 1 is a perspective view of a main part showing a first example of a best mode for carrying out a gear according to the present invention.
  • FIG. 2 is a cross-sectional view of the mating state of FIG.
  • FIG. 3 is a diagram showing the start of the application of the lubricating oil in the combined state of FIG.
  • FIG. 4 is a diagram showing a lubricating oil application process following FIG.
  • FIG. 5 is a diagram showing a lubricating oil application process following FIG.
  • FIG. 6 is a diagram showing a lubricating oil application process following FIG.
  • FIG. 7 is a sectional view of a main part showing a second example of the best mode for carrying out the gear according to the present invention.
  • FIG. 8 shows a third example of the best mode for carrying out the gear according to the present invention. It is sectional drawing of the principal part shown.
  • FIG. 9 is a perspective view of a main part showing a fourth example of the best mode for carrying out the gear according to the present invention.
  • FIG. 10 is a sectional view of a main part showing a fifth example of the best mode for carrying out the gear according to the present invention.
  • FIG. 11 is a graph of an experiment for clarifying the effectiveness of the best mode for implementing the gear according to the present invention.
  • 1 to 6 show a first example of a best mode for implementing a gear according to the present invention.
  • the groove 2 provided in the tooth surface 1 is located near the end of the tooth surface 3 side of the effective surface S.
  • the space for providing the groove 2 can be secured by using so-called high teeth.
  • the groove 2 of the first example is a continuous depression having a semicircular cross section, and one groove is disposed linearly over the entire width of the tooth width.
  • the groove 2 has a groove width, groove depth, etc. determined according to the degree of viscosity, viscosity, surface tension, etc. of the used lubricant G (for example, lithium-based grease). Can be stored.
  • the machining means of the groove 2 one-piece molding, engraving after molding and the like are selected according to the material to be formed.
  • the molding material of the first example has properties that can slightly deform the groove 2 at the time of joining. This elasticity can be easily obtained by using a synthetic resin material as the forming material.
  • the groove 2 has a tooth surface 1 Since the teeth are not located near the pitch circle R, the strength of the teeth cannot be reduced.Also, the bending of the teeth is likely to occur at the position where the groove 2 receives the stress of sliding friction instead of the stress of rolling friction. Since it is not located in the fillet of the tooth root, there is no danger of chipping or cracking near the groove 2 even if it is used for a long time.
  • the lubricating oil G flowing out to each tooth surface 1 is extended by the relative slippage of the tooth surfaces 1 and the contact surface pressure with the progress of the mutual rotation, and each other. It is supplied so that it is applied with a constant film thickness on the tooth surface 1. Therefore, the lubricating oil G is effectively supplied to the tooth surface 1 without the lubricating oil G being removed from the tooth surface 1 as in the conventional example described above. Since the groove 2 is provided over the entire width of the tooth width, there is no uneven supply of the lubricating oil G to the tooth surface 1.
  • the present inventors have confirmed through various experiments that the durability time is extended by 20 to 30% as compared with the case where the groove 2 is not provided.
  • the groove 2 is not provided near the pitch circle R, there is little contact deformation at the pitch circle R where the tooth surface load is the highest, and the continuity of the interface is effectively ensured.
  • the rotational transmission error is reduced with the improvement.
  • generation of noise abnormal noise
  • the vicinity of the groove 2 provided on the other tooth surface 1 comes into contact with the tooth root 4 side of the one tooth surface 1, and the groove is formed as described above.
  • the lubricating oil G accumulated in 2 is pushed out and flows out to each tooth surface 1.
  • the lubricating oil G is applied toward the pitch circle R by the relative slippage of the tooth surface 1 and the contact surface pressure when the tooth surface 1 has an involute curve.
  • FIG. 7 shows a second example of the best mode for carrying out the gear according to the present invention.
  • the grooves 2 of the first example described above are located near both ends of the effective end surface S of the tooth flank 3 and the tooth root 4 before and after rotation. .
  • the grooves 2 located near both ends of the tooth flank 3 and the tooth root 4 face each other, and the lubricating oil G accumulated in the grooves 2 is pressed. As a result, the lubricating oil G flows smoothly from the groove 2 to the tooth surface 1. In addition, since the supply of the lubricating oil G to the above-mentioned tooth surface 1 is performed in a complicated and complex manner in the opposite direction on both sides before and after rotation, a high degree of lubrication is maintained for the entire gear.
  • FIG. 8 shows a third example of the best mode for carrying out the gear according to the present invention.
  • the grooves 2 of the second example are arranged in two rows.
  • the recesses in each row of the groove 2 are made different in groove width and groove depth so that the amount of lubricating oil G that accumulates gradually toward the pitch circle (almost the center of the mating effective surface S) is reduced. Is formed.
  • the amount of the lubricating oil G that can be stored with the total volume of the two rows of grooves 2 can be increased. Also, how to supply lubricant G to tooth surface 1 By reducing the amount of lubricating oil G stored in the direction, the supply of lubricating oil G to the tooth surface 1 is prevented from becoming excessive.
  • FIG. 9 shows a fourth example of the best mode for carrying out the gear according to the present invention.
  • the grooves 2 of the third example described above are formed as a large number of rows of fine grooves.
  • the depressions in each row of the grooves 2 are formed so that the amount of the lubricant G accumulated toward the pitch circle is gradually reduced by varying the groove width, groove depth, and interval.
  • a machining means of the groove 2 for example, wire cut electric discharge machining can be considered.
  • the interface ratio when the interface ratio is small (for example, when the interface ratio is very close to 1 (the effective surface S is small), a large concave groove 2 is formed close to the pitch circle. Therefore, it is suitable for the case where the contact ratio is small and the continuity of the contact cannot be maintained by the groove 2 or for preventing the reduction of the tooth strength.
  • FIG. 10 shows a fifth example of the best mode for carrying out the gear according to the present invention.
  • the grooves 2 of the fourth example described above are intermittently discontinuous, and the depressions of the grooves 2 in each row are arranged in a staggered manner. Electricity, shot peening, transfer and the like can be considered as means for machining the groove 2.
  • the staggered arrangement of the grooves 2 in each row is arranged substantially over the entire tooth width, uneven supply of the lubricating oil G to the tooth surface 1 may occur. Absent.
  • the grooves 2 in a strip shape with dimples or the like.
  • the depression of the groove 2 is formed so that the dimple diameter and the dimple depth are made different so that the amount of the lubricating oil G accumulated toward the pitch circle gradually decreases.
  • the groove 2 can be provided up to the pitch circle R.
  • FIG. 11 shows experimental results for clarifying the effectiveness of the gear according to the present invention.
  • a module 1 a tooth width of 5 mm, and a number of teeth of 30 to 31 were combined with a gear formed of a synthetic resin material made of polyacetal (POM).
  • the chain line shows the standard case without the groove 2.
  • the solid line shows the case where one groove 2 is provided on the drive end side and the driven end end side so that the contact ratio becomes 1 or more.
  • a comparative test was carried out using a combined rotation with a gear load of 40 N / mm and a pitch circumferential speed of 1 mZS.
  • the lubricating oil used was a rare resin-based grease.
  • the groove 2 a circular arc cross sectional shape, and a width 0. 2 mm, depth 0 7 mm, the groove volume 0. 0 5 mm 3.
  • the vertical axis shows the temperature
  • the horizontal axis shows the total number of revolutions before the gear breaks. It can be understood that when one groove 2 is provided on the tooth end side, the temperature range around 50 is maintained for a long time, and the durability performance is enhanced.
  • the groove 2 may be provided only on the root side of the tooth surface 1.
  • the present invention can be applied to helical gears, worm gears, and the like.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)

Abstract

A rather small gear having a lubricating structure capable of uniformly and effectively supplying lubricating oil to tooth faces without lowering the strength of gear teeth while maintaining the continuity of engagement of the gear teeth and also having a relative sliding in the engagement of the gear teeth, characterized in that, in the gear having grooves (2) for accumulating the lubricating oil formed in the tooth faces (1), the grooves (2) are positioned near the addendum (3) side end parts of the working surfaces of the tooth faces (1) through the entire tooth width, whereby the lubricating oil accumulated in the grooves positioned on the addendum sides apart from the pitch circle of the tooth faces is forced out by the continuous engagement of the gear teeth and fed so as to be applied to the entire width of the tooth faces by the relative sliding of and the contact surface pressure on the tooth faces.

Description

明 細 書 歯車 技術分野  Description Gear Technical field
本発明は、 潤滑構造を備え歯の嚙合いで相対滑りのある比較的小型の 歯車に関する。 背景技術  The present invention relates to a relatively small gear having a lubricating structure and having relative slippage between teeth. Background art
最近、 歯車の形成材料として、 金属材， 合成樹脂材， ゴム材， 金属一 合成樹脂複合材等のように多種多様のものが提供されてきている。 そし て、 歯車の嚙合いでは、 いずれの形成材料についても、 嚙合い騒音， 温 度上昇を抑制して耐久性を高めるために潤滑油の使用が有効であると されている。  Recently, a wide variety of gear forming materials have been provided, such as metal materials, synthetic resin materials, rubber materials, and metal-synthetic resin composite materials. In addition, in the case of gears, it is said that the use of lubricating oil is effective for suppressing the noise and temperature rise and increasing the durability of all materials.
比較的大型の歯車の嚙合いでは、 例えば、 潤滑油を歯車の歯面に噴射 する潤滑油噴射機構が歯車に近接して備えられる。 また、 比較的小型の 歯車の嚙合いでは、 例えば、 潤滑油を封入したギアボックスの内部に収 容された歯車の歯面における潤滑油の枯渴を防止する潤滑構造が歯車 自体に備えられる。  In the case of a relatively large gear, for example, a lubricating oil injection mechanism that injects lubricating oil to the gear tooth surface is provided close to the gear. In addition, in the case of a relatively small gear, for example, the gear itself is provided with a lubricating structure for preventing the lubricating oil from running out on the tooth surfaces of the gear contained in the gear box filled with the lubricating oil.
従来、 潤滑構造を備えた比較的小型の歯車としては、 例えば、 実開平 4 - 5 8 6 5 4号公報に記載のものが知られている。  Conventionally, as a relatively small gear having a lubricating structure, for example, a gear described in Japanese Utility Model Laid-Open No. 4-58685 is known.
この従来の歯車は、 歯面のピッチ円付近に歯幅の端部から部分的に切 欠き形成された溝が設けられてなる。  This conventional gear is provided with a groove partially cut out from the end of the tooth width near the pitch circle of the tooth surface.
この従来の歯車によると、 溝に溜められた潤滑油に嚙合う歯面が接触 することで、 歯面に適時潤滑油が供給されて歯面における潤滑油の枯渴 が防止される。 また、 溝を歯幅の一部にのみ設けることで、 嚙合いの連 続性が損なわれるのを防止している。  According to this conventional gear, the lubricating oil matching the lubricating oil stored in the groove is brought into contact with the lubricating oil, so that the lubricating oil is supplied to the tooth surface in a timely manner, thereby preventing the lubricating oil from running out on the tooth surface. Also, by providing the groove only in a part of the tooth width, the continuity of the connection is prevented from being impaired.
前述の従来の歯車では、 溝が嚙合いの転がり摩擦の応力を受ける歯面 のピッチ円付近に位置しているため、 歯の強度が低下してしまうという 問題点がある。また、溝が歯幅の一部にしか設けられていないことから、 歯面への潤滑油の供給にむらが生じてしまうという問題点がある。 また、 溝が歯面の嚙合い有効面 （歯面同士の接触面） の中途部に位置している ため、 歯面の滑り摩擦の際に逆に溝が歯面から潤滑油を搔取ってしまう という問題点がある。 発明の開示 In the above-mentioned conventional gears, the grooves are located near the pitch circle of the tooth surface that receives the stress of the rolling friction, which reduces the strength of the teeth. There is a problem. Further, since the grooves are provided only in a part of the tooth width, there is a problem that the supply of the lubricating oil to the tooth surface becomes uneven. Also, since the groove is located in the middle of the mating effective surface (contact surface between the tooth surfaces), the groove conversely removes lubricating oil from the tooth surface when sliding friction occurs on the tooth surface. There is a problem. Disclosure of the invention
本発明は、 前述の問題点を考慮してなされたもので、 嚙合いの連続性 を維持しつつ、 歯の強度を低下させることなく潤滑油を歯面にむらなく 有効に供給することのできる潤滑構造を備えた歯車を提供することを 技術的課題とする。  The present invention has been made in consideration of the above-described problems, and can effectively supply lubricating oil evenly to the tooth surface without lowering the strength of the teeth while maintaining the continuity of the connection. A technical problem is to provide a gear having a lubricating structure.
この技術的課題の解決方法は、 請求の範囲 1に記載のように、 歯面に 潤滑油を溜める溝が設けられた歯車において、 溝は歯面の嚙合い有効面 の歯末側の端部付近に位置され歯幅の全幅に配設されていることを特 徴とする歯車として構成される。  According to a method for solving this technical problem, as described in claim 1, in a gear provided with a groove for storing lubricating oil on a tooth surface, the groove is formed at an apical end of a mating effective surface of the tooth surface. It is configured as a gear that is characterized by being located in the vicinity of the entire width of the tooth width.
この解決方法によると、 歯面のピッチ円から離れて歯末側に位置され た溝に溜められた潤滑油が連続した嚙合いで押出され歯面の相対滑り 接触面圧力とで互いの歯面の歯幅の全幅に塗布するように供給される。 即ち、 溝が歯面の嚙合い有効面の歯末側の端部付近に位置され、 歯面の ピッチ円から離れて位置されているため、 嚙合いの連続性が維持される とともに歯の強度が低下することがない。 また、 溝が歯幅の全幅に配設 されているため、 歯面への潤滑油の供給にむらが生じない。 また、 溝が 歯面の嚙合い有効面の歯末側の端部付近に位置され、 潤滑油が歯面の相 対滑りと接触面圧力とで互いの歯面に塗布するように供給されるため、 潤滑油が歯面に有効に供給される。  According to this solution, the lubricating oil stored in the groove located at the end of the tooth apart from the pitch circle of the tooth surface is extruded in a continuous manner and the relative sliding of the tooth surfaces is caused by the contact surface pressure and the mutual tooth surface. Is supplied so as to be applied to the entire width of the tooth width. That is, since the groove is located near the end of the tooth flank on the tooth flank side and away from the pitch circle of the tooth flank, the continuity of the tooth flank is maintained and the tooth strength is maintained. Does not decrease. In addition, since the grooves are provided over the entire width of the teeth, there is no uneven supply of lubricating oil to the tooth surfaces. In addition, the groove is located near the end of the tooth flank on the mating effective surface, and lubricating oil is supplied so as to be applied to the tooth flank by the relative sliding of the tooth flank and the contact surface pressure. Therefore, lubricating oil is effectively supplied to the tooth surface.
この技術的課題の他の解決方法は、 請求の範囲 2に記載のように、 歯 面に潤滑油を溜める溝が設けられた歯車において、 溝は歯面の嚙合い有 効面の歯元側の端部付近に位置され歯幅の全幅に配設されていること を特徴とする歯車として構成される。 この解決方法によると、 歯面のピッチ円から離れて歯元側に位置され た溝に溜められた潤滑油が連続した嚙合いで押出され歯面の相対滑り と接触面圧力とで互いの歯面の歯幅の全幅に塗布するように供給され る。 即ち、 溝が歯面の嚙合い有効面の歯元側の端部付近に位置され、 歯 面のピッチ円から離れて位置されているため、 嚙合いの連続性が維持さ れるとともに歯の強度が低下することがない。 また、 溝が歯幅の全幅に 配設されているため、 歯面への潤滑油の供給にむらが生じない。 また、 溝が歯面の嚙合い有効面の歯元側の端部付近に位置され、 潤滑油が歯面 の相対滑りと接触面圧力とで互いの歯面に塗布するように供給される ため、 潤滑油が歯面に有効に供給される。 Another solution to this technical problem is, as described in claim 2, in a gear provided with a groove for storing lubricating oil on a tooth surface, wherein the groove is formed on the tooth root side of the effective surface of the tooth surface. The gear is characterized in that it is located near the end of the gear and is disposed over the entire width of the tooth width. According to this solution, the lubricating oil accumulated in the groove located on the root side away from the pitch circle of the tooth surface is extruded in a continuous manner, and the mutual lubrication of the tooth surface and the contact surface pressure cause the mutual lubrication. Supplied so as to apply to the entire width of the face. That is, since the groove is located near the end of the tooth surface on the root side of the mating effective surface and is located away from the pitch circle of the tooth surface, the continuity of the mating is maintained and the tooth strength is maintained. Does not decrease. In addition, since the grooves are provided over the entire width of the teeth, there is no uneven supply of lubricating oil to the tooth surfaces. In addition, the groove is located near the root end of the mating effective surface of the tooth surface, and lubricating oil is supplied so as to be applied to each tooth surface by the relative sliding of the tooth surface and the contact surface pressure. However, lubricating oil is effectively supplied to the tooth surface.
この技術的課題の他の解決方法は、 請求の範囲 3に記載のように、 請 求の範囲 1または 2の歯車において、 溝は歯幅の全幅に連続した窪みと して直線状に配設されていることを特徴とする歯車として構成される。 この解決方法によると潤滑油が歯幅の全幅に連続して直線状に溜め られる。  Another solution to this technical problem is, as described in claim 3, in the gear of claim 1 or 2, wherein the grooves are linearly arranged as depressions continuous to the entire width of the tooth width. It is constituted as a gear characterized by being carried out. According to this solution, the lubricating oil is stored linearly continuously over the entire tooth width.
この技術的課題の他の解決方法は、 請求の範囲 4に記載のように、 請 求の範囲 1または 2の歯車において、 溝は歯幅の全幅に間欠した窪みと して直線状に配設されていることを特徴とする歯車として構成される。 この解決方法によると、 潤滑油が歯幅の全幅に間欠して直線状に溜め られる。  Another solution to this technical problem is, as described in claim 4, in the gear of claim 1 or 2, wherein the groove is linearly arranged as a recess intermittently over the entire width of the tooth width. It is constituted as a gear characterized by being carried out. According to this solution, the lubricating oil is intermittently accumulated in the entire width of the tooth width and is linearly accumulated.
この技術的課題の他の解決方法は、 請求の範囲 5に記載のように、 請 求の範囲 3または 4の歯車において、 溝は複数列に並列されていること を特徴とする歯車として構成される。  Another solution to this technical problem is, as described in claim 5, configured as a gear in claim 3 or 4, wherein the grooves are arranged in a plurality of rows in parallel. You.
この解決方法によると、 潤滑油が複数列に溜められる。  According to this solution, the lubricating oil is stored in multiple rows.
この技術的課題の他の解決方法は、 請求項 6に記載のように、 請求の 範囲 5の歯車において、 溝の各列の窪みはピッチ円に向けて潤滑油を溜 める量が順次少なくなるように形成されていることを特徴とする歯車 として構成される。  Another solution to this technical problem is that, as described in claim 6, in the gear of claim 5, the recess in each row of the groove has a gradually decreasing amount of lubricating oil accumulated toward the pitch circle. The gear is characterized in that it is formed as follows.
この解決方法によると、 複数列に溜められる潤滑油の量がピッチ円に 向けて順次少なくなる。 According to this solution, the amount of lubricating oil stored in multiple rows It decreases sequentially toward.
この技術的課題の他の解決方法としては、 請求の範囲 7に記載のよう に、 請求の範囲 1または 2の歯車において、 溝は歯幅の全幅に散点した 微小な窪みとして帯状に配設されていることを特徴とする歯車として 構成される。  As another solution to this technical problem, as described in claim 7, in the gear of claim 1 or 2, the grooves are arranged in a band shape as minute recesses scattered over the entire width of the tooth width. It is configured as a gear that is characterized by
この解決方法によると、 潤滑油が歯幅の全幅に散点して溜められる。 この技術的課題の他の解決方法としては、 請求の範囲 8に記載のよう に、 請求の範囲 7の歯車において、 溝の窪みはピッチ円に向けて潤滑油 を溜める量が順次少なくなるように形成されていることを特徴とする 歯車として構成される。  According to this solution, the lubricating oil is scattered and stored over the entire tooth width. As another solution to this technical problem, as described in claim 8, in the gear of claim 7, the recess of the groove is such that the amount of lubricating oil accumulated in the pitch circle gradually decreases. It is configured as a gear characterized by being formed.
この解決方法によると、 散点して溜められる潤滑油の量がピッチ円に 向けて順次少なくなる。  According to this solution, the amount of lubricating oil that is accumulated as scattered points gradually decreases toward the pitch circle.
この技術的課題の他の解決方法としては、 請求の範囲 9に記載のよう に、 請求の範囲 1〜 8のいずれかの歯車において、 形成材料は嚙合いで 歯面の嚙合い有効面の歯末側の端部付近に位置された溝を僅かに変形 させる弾性を有していることを特徴とする歯車として構成される。  As another solution of this technical problem, as described in claim 9, in any one of the gears according to claims 1 to 8, the forming material is different and the tooth of the effective surface of the tooth surface is different. The gear is characterized by having elasticity to slightly deform the groove located near the end on the rear side.
この解決方法によると、 潤滑油が溝の弾性変形で押出される。 図面の簡単な説明  According to this solution, the lubricating oil is pushed out by the elastic deformation of the groove. BRIEF DESCRIPTION OF THE FIGURES
第 1図は、 本発明に係る歯車を実施するための最良の形態の第 1例を 示す要部の斜視図である。  FIG. 1 is a perspective view of a main part showing a first example of a best mode for carrying out a gear according to the present invention.
第 2図は、 第 1図の嚙合い状態の断面図である。  FIG. 2 is a cross-sectional view of the mating state of FIG.
第 3図は、 第 2図の嚙合い状態の潤滑油の塗布始めを示す図である。 第 4図は、 第 3図に続く潤滑油の塗布過程を示す図である。  FIG. 3 is a diagram showing the start of the application of the lubricating oil in the combined state of FIG. FIG. 4 is a diagram showing a lubricating oil application process following FIG.
第 5図は、 第 4図に続く潤滑油の塗布過程を示す図である。  FIG. 5 is a diagram showing a lubricating oil application process following FIG.
第 6図は、 第 5図に続く潤滑油の塗布過程を示す図である。  FIG. 6 is a diagram showing a lubricating oil application process following FIG.
第 7図は、 本発明に係る歯車を実施するための最良の形態の第 2例を 示す要部の断面図である。  FIG. 7 is a sectional view of a main part showing a second example of the best mode for carrying out the gear according to the present invention.
第 8図は、 本発明に係る歯車を実施するための最良の形態の第 3例を 示す要部の断面図である。 FIG. 8 shows a third example of the best mode for carrying out the gear according to the present invention. It is sectional drawing of the principal part shown.
第 9図は、 本発明に係る歯車を実施するための最良の形態の第 4例を 示す要部の斜視図である。  FIG. 9 is a perspective view of a main part showing a fourth example of the best mode for carrying out the gear according to the present invention.
第 1 0図は、 本発明に係る歯車を実施するための最良の形態の第 5例 を示す要部の断面図である。  FIG. 10 is a sectional view of a main part showing a fifth example of the best mode for carrying out the gear according to the present invention.
第 1 1図は、 本発明に係る歯車を実施するための最良の形態の有効性 を明らかにする実験のグラフである。 発明を実施するための最良の形態  FIG. 11 is a graph of an experiment for clarifying the effectiveness of the best mode for implementing the gear according to the present invention. BEST MODE FOR CARRYING OUT THE INVENTION
以下、 本発明に係る歯車を実施するための最良の形態を図面に基づい て説明する。  Hereinafter, the best mode for carrying out the gear according to the present invention will be described with reference to the drawings.
第 1図〜第 6図は、 本発明に係る歯車を実施するための最良の形態の 第 1例を示すものである。  1 to 6 show a first example of a best mode for implementing a gear according to the present invention.
第 1例では、 第 1図， 第 2図に示すように、 平歯車からなるものが示 されている。  In the first example, as shown in FIGS. 1 and 2, a spur gear is shown.
第 1例は、 前述の従来例とは異なって、 歯面 1に設けられる溝 2が嚙 合い有効面 Sの歯末 3側の端部付近に位置されている。 なお、 嚙合い率 が 1にかなり近い場合には、 歯をいわゆる高歯とすることで溝 2を設け るスペースを確保することができる。  In the first example, unlike the above-described conventional example, the groove 2 provided in the tooth surface 1 is located near the end of the tooth surface 3 side of the effective surface S. When the contact ratio is fairly close to 1, the space for providing the groove 2 can be secured by using so-called high teeth.
第 1例の溝 2は、 断面が半円形の連続した窪みからなるもので、 歯幅 の全幅にわたり直線状に 1本が配設されている。 この溝 2は、 使用され る潤滑油 G (例えば、 リチウム系のグリス） のちよう度， 粘度， 表面張 力等に対応して、 溝幅， 溝深さ等が決定され、 内部に潤滑油 Gを溜める ことができるようになつている。 この溝 2の工作手段については、 形成 材料に対応して一体成形， 成形後の刻設等が選択される。  The groove 2 of the first example is a continuous depression having a semicircular cross section, and one groove is disposed linearly over the entire width of the tooth width. The groove 2 has a groove width, groove depth, etc. determined according to the degree of viscosity, viscosity, surface tension, etc. of the used lubricant G (for example, lithium-based grease). Can be stored. As the machining means of the groove 2, one-piece molding, engraving after molding and the like are selected according to the material to be formed.
第 1例の成形材材料は、 嚙合いの際に溝 2を僅かに変形させることが 可能な弹性を有している。 この弾性については、 形成材料を合成樹脂材 とすることで容易に得ることができる。  The molding material of the first example has properties that can slightly deform the groove 2 at the time of joining. This elasticity can be easily obtained by using a synthetic resin material as the forming material.
第 1例によると、 溝 2が嚙合いの転がり摩擦の応力を受ける歯面 1の ピッチ円 R付近に位置していないため、 歯の強度を低下させることがな レ また、 溝 2が嚙合いの転がり摩擦の応力ではなく滑り摩擦の応力を 受ける位置で歯の曲げ折損の生じやすい歯元すみ肉部に位置しないた め、 長期に使用しても溝 2付近で欠損， ひび割れ等が生じるおそれはな レ 。 According to the first example, the groove 2 has a tooth surface 1 Since the teeth are not located near the pitch circle R, the strength of the teeth cannot be reduced.Also, the bending of the teeth is likely to occur at the position where the groove 2 receives the stress of sliding friction instead of the stress of rolling friction. Since it is not located in the fillet of the tooth root, there is no danger of chipping or cracking near the groove 2 even if it is used for a long time.
第 1例の嚙合いの回転では、 第 3図に示すように、 嚙合いの初期段階 で歯末 3側に位置する溝 2付近が他方の歯面 1の歯元 4側に当接する ことになる。 この結果、 溝 2に溜まっている潤滑油 Gが外部に押出され て互いの歯面 1に流出する。 このとき、 歯元 4側から歯末 3側に掛かる 嚙合いの応力 Pで歯末 3側が僅かに弾性変形するのに伴って、 溝 2も僅 かに弾性変形して前述の溝 2からの潤滑油 Gの押出しが助勢される。 なお、 溝 2に溜まっている潤滑油 Gは、 溝 2が歯底 5に向けて侵入し た際に、歯底 5に滞溜している潤滑油 Gを搔出したものである。従って、 歯底 5に滞溜している潤滑油 Gが長時間その状態に放置されて熱等で 劣化することがなくなる。  In the first example of rotation, as shown in Fig. 3, in the initial stage of the engagement, the vicinity of the groove 2 located on the tooth tip 3 side comes into contact with the tooth root 4 side of the other tooth surface 1 Become. As a result, the lubricating oil G stored in the groove 2 is pushed out and flows out to the tooth surfaces 1 of each other. At this time, as the tooth end 3 side is slightly elastically deformed by the combined stress P applied from the tooth root 4 side to the tooth end 3 side, the groove 2 is also slightly elastically deformed, and the groove 2 Extrusion of lubricating oil G is assisted. The lubricating oil G accumulated in the groove 2 is obtained by extracting the lubricating oil G accumulated in the tooth bottom 5 when the groove 2 enters the tooth bottom 5. Therefore, the lubricating oil G staying at the tooth bottom 5 is not left in that state for a long time and does not deteriorate due to heat or the like.
続いて、 第 4図に示すように、 互いの歯面 1に流出した潤滑油 Gが嚙 合いの回転の進行に伴って歯面 1同士の相対滑りと接触面圧力とで引 延ばされ互いの歯面 1に一定の膜厚で塗布するように供給されていく。 従って、 前述の従来例のように潤滑油 Gが歯面 1から搔取られるような こともなく、 潤滑油 Gが歯面 1に有効に供給される。 なお、 溝 2が歯幅 の全幅に配設されているため、 歯面 1への潤滑油 Gの供給にむらが生じ ることがない。  Subsequently, as shown in FIG. 4, the lubricating oil G flowing out to each tooth surface 1 is extended by the relative slippage of the tooth surfaces 1 and the contact surface pressure with the progress of the mutual rotation, and each other. It is supplied so that it is applied with a constant film thickness on the tooth surface 1. Therefore, the lubricating oil G is effectively supplied to the tooth surface 1 without the lubricating oil G being removed from the tooth surface 1 as in the conventional example described above. Since the groove 2 is provided over the entire width of the tooth width, there is no uneven supply of the lubricating oil G to the tooth surface 1.
従って、 嚙合いによる摩擦発熱のための歯の温度上昇が抑制され、 曲 げ強度の低下や摩耗が抑制され、 耐久性が大きく向上する。 本発明者等 は、 各種の実験によって、 溝 2のない場合に比して 2 0〜 3 0 %の耐久 時間の延長を確認している。 また、 ピッチ円 R付近に溝 2が設けられて いないため、 嚙合いで最も歯面荷重の高いピッチ円 Rでの接触変形が少 なくて嚙合いの連続性が有効に確保され、 耐久性の向上とともに回転伝 達誤差が低減される。また、嚙合いに良好な潤滑状態が維持されるため、 騒音 （異音） の発生が低減される。 Therefore, a rise in the temperature of the teeth due to frictional heating due to the combination is suppressed, a decrease in bending strength and wear are suppressed, and durability is greatly improved. The present inventors have confirmed through various experiments that the durability time is extended by 20 to 30% as compared with the case where the groove 2 is not provided. In addition, since the groove 2 is not provided near the pitch circle R, there is little contact deformation at the pitch circle R where the tooth surface load is the highest, and the continuity of the interface is effectively ensured. The rotational transmission error is reduced with the improvement. In addition, since a good lubrication state is maintained, Generation of noise (abnormal noise) is reduced.
そして、第 5図に示すように、嚙合いがピッチ円 Rに到達した段階で、 溝 2から押出された潤滑油 Gを歯面 1の相対滑りと接触面圧力とによ る引延ばしの塗布が終了する。 この後の嚙合いの回転の進行では、 先の 塗布等で歯面 1に残留している潤滑油 Gを歯面 1の相対滑りと接触面 圧力とで平坦化する。  Then, as shown in FIG. 5, when the contact reaches the pitch circle R, the lubricating oil G extruded from the groove 2 is spread by the relative sliding of the tooth surface 1 and the contact surface pressure. Ends. In the subsequent rotation progress, the lubricating oil G remaining on the tooth surface 1 due to the previous application or the like is flattened by the relative sliding of the tooth surface 1 and the contact surface pressure.
さらに、 嚙合いが進行すると、 第 6図に示すように、 他方の歯面 1に 設けられている溝 2付近が一方の歯面 1の歯元 4側に当接し、 前述と同 様に溝 2に溜まっている潤滑油 Gが外部に押出されて互いの歯面 1に 流出する。 この潤滑油 Gは、 歯面 1がインポリュート曲線の場合に、 歯 面 1の相対滑りと接触面圧力とでピッチ円 Rに向けて塗布される。  Further, as the contact progresses, as shown in FIG. 6, the vicinity of the groove 2 provided on the other tooth surface 1 comes into contact with the tooth root 4 side of the one tooth surface 1, and the groove is formed as described above. The lubricating oil G accumulated in 2 is pushed out and flows out to each tooth surface 1. The lubricating oil G is applied toward the pitch circle R by the relative slippage of the tooth surface 1 and the contact surface pressure when the tooth surface 1 has an involute curve.
第 7図は、 本発明に係る歯車を実施するための最良の形態の第 2例を 示すものである。  FIG. 7 shows a second example of the best mode for carrying out the gear according to the present invention.
第 2例では、 前述の第 1例の溝 2が回転の前後の両歯面 1の嚙合い有 効面 Sの歯末 3側， 歯元 4側の双方の端部付近に位置されている。  In the second example, the grooves 2 of the first example described above are located near both ends of the effective end surface S of the tooth flank 3 and the tooth root 4 before and after rotation. .
第 2例によると、 歯末 3側， 歯元 4側の双方の端部付近に位置されて いる溝 2同士が嚙合いで対面し、 互いの溝 2に溜まっている潤滑油 Gが 圧迫されて押出されるため、 溝 2から歯面 1への潤滑油 Gの流出が円滑 になる。 また、 前述の歯面 1への潤滑油 Gの供給が回転の前後両側で逆 方向から複雑， 複合的に行われるため、 歯車全体に高度の潤滑性が維持 される。  According to the second example, the grooves 2 located near both ends of the tooth flank 3 and the tooth root 4 face each other, and the lubricating oil G accumulated in the grooves 2 is pressed. As a result, the lubricating oil G flows smoothly from the groove 2 to the tooth surface 1. In addition, since the supply of the lubricating oil G to the above-mentioned tooth surface 1 is performed in a complicated and complex manner in the opposite direction on both sides before and after rotation, a high degree of lubrication is maintained for the entire gear.
第 8図は、 本発明に係る歯車を実施するための最良の形態の第 3例を 示すものである。  FIG. 8 shows a third example of the best mode for carrying out the gear according to the present invention.
第 3例では、 第 2例の溝 2を 2列に並列させている。 そして、 溝 2の 各列の窪みは、 溝幅， 溝深さを異ならせることでピッチ円 （嚙合い有効 面 Sのほぼ中央部） に向けて潤滑油 Gを溜める量が順次少なくなるよう に形成されている。  In the third example, the grooves 2 of the second example are arranged in two rows. The recesses in each row of the groove 2 are made different in groove width and groove depth so that the amount of lubricating oil G that accumulates gradually toward the pitch circle (almost the center of the mating effective surface S) is reduced. Is formed.
第 3例によると、 2列の溝 2の合計の容積で溜めることのできる潤滑 油 Gの量を増量することができる。 また、 潤滑油 Gの歯面 1への供給方 向で溜められている潤滑油 Gの量が少なくなることで、 歯面 1への潤滑 油 Gの供給が過剰になるのを防止する。 According to the third example, the amount of the lubricating oil G that can be stored with the total volume of the two rows of grooves 2 can be increased. Also, how to supply lubricant G to tooth surface 1 By reducing the amount of lubricating oil G stored in the direction, the supply of lubricating oil G to the tooth surface 1 is prevented from becoming excessive.
第 9図は、 本発明に係る歯車を実施するための最良の形態の第 4例を 示すものである。  FIG. 9 shows a fourth example of the best mode for carrying out the gear according to the present invention.
第 4例では、 前述の第 3例の溝 2を多数列の微細溝としてある。 この 溝 2の各列の窪みは、 溝幅， 溝深さ， 間隔を異ならせることでピッチ円 に向けて潤滑油 Gを溜める量が順次少なくなるように形成されている。 この溝 2の工作手段としては、 例えば、 ワイアカット放電加工が考えら れる。  In the fourth example, the grooves 2 of the third example described above are formed as a large number of rows of fine grooves. The depressions in each row of the grooves 2 are formed so that the amount of the lubricant G accumulated toward the pitch circle is gradually reduced by varying the groove width, groove depth, and interval. As a machining means of the groove 2, for example, wire cut electric discharge machining can be considered.
第 4例によると、 嚙合い率が小さい （例えば、 嚙合い率 1にかなり近 レ 場合 （嚙合い有効面 Sが小さい） に、 ピッチ円に近接して大きな窪 みの溝 2が形成されるのを避けることができるため、 嚙合い率が小さく 嚙合いの連続性が溝 2により維持できなくなる場合や歯の強度の低下 の防止の場合に好適となる。  According to the fourth example, when the interface ratio is small (for example, when the interface ratio is very close to 1 (the effective surface S is small), a large concave groove 2 is formed close to the pitch circle. Therefore, it is suitable for the case where the contact ratio is small and the continuity of the contact cannot be maintained by the groove 2 or for preventing the reduction of the tooth strength.
第 1 0図は、 本発明に係る歯車を実施するための最良の形態の第 5例 を示すものである。  FIG. 10 shows a fifth example of the best mode for carrying out the gear according to the present invention.
第 5例では、 前述の第 4例の溝 2を連続させずに間欠させるとともに、 各列の溝 2の窪みを千鳥状に配置してある。 この溝 2の工作手段として は、 電铸， ショットピーニング， 転写等が考えられる。  In the fifth example, the grooves 2 of the fourth example described above are intermittently discontinuous, and the depressions of the grooves 2 in each row are arranged in a staggered manner. Electricity, shot peening, transfer and the like can be considered as means for machining the groove 2.
第 5例によると、 各列の溝 2の千鳥状の配置が実質的に歯幅の全幅に 配設されたことになるため、 歯面 1への潤滑油 Gの供給にむらが生じる ことがない。  According to the fifth example, since the staggered arrangement of the grooves 2 in each row is arranged substantially over the entire tooth width, uneven supply of the lubricating oil G to the tooth surface 1 may occur. Absent.
第 5例の変形例としては、 溝 2をディンプル等で帯状に散点させる配 置することが考えられる。 この溝 2の窪みは、 ディンプル径， ディンプ ル深さを異ならせることでピッチ円に向けて潤滑油 Gを溜める量が順 次少なくなるように形成されている。 なお、 溝 2が微小化された場合、 溝 2をピッチ円 Rにまで設けることもできる。  As a modified example of the fifth example, it is conceivable to dispose the grooves 2 in a strip shape with dimples or the like. The depression of the groove 2 is formed so that the dimple diameter and the dimple depth are made different so that the amount of the lubricating oil G accumulated toward the pitch circle gradually decreases. When the groove 2 is miniaturized, the groove 2 can be provided up to the pitch circle R.
第 1 1図は、 本発明に係る歯車の有効性を明らかにするための実験結 果を示している。 この実験は、 モジュール 1， 歯幅 5 mm， 歯数 3 0枚— 3 1枚のポリ ァセタール （P O M) からなる合成樹脂材で成形した歯車を組合わせて いる。 鎖線で図示されているのは、 溝 2を設けない標準の場合である。 実線で図示されているのは、 溝 2を嚙合い率が 1以上になるように駆動 側， 従動側の歯末側に 1本設けた場合である。 FIG. 11 shows experimental results for clarifying the effectiveness of the gear according to the present invention. In this experiment, a module 1, a tooth width of 5 mm, and a number of teeth of 30 to 31 were combined with a gear formed of a synthetic resin material made of polyacetal (POM). The chain line shows the standard case without the groove 2. The solid line shows the case where one groove 2 is provided on the drive end side and the driven end end side so that the contact ratio becomes 1 or more.
この実験では、 歯車荷重 4 0 N/mm， ピッチ円周速度 1 mZ Sでの 嚙合い回転により比較試験したものである。 なお、 潤滑油としては、 ゥ レア樹脂系グリスを採用した。 また、 溝 2は、 断面円弧形の形状とし、 幅 0 . 2 mm， 深さ 0 7 mm, 溝容積 0 . 0 5 mm 3とした。 In this experiment, a comparative test was carried out using a combined rotation with a gear load of 40 N / mm and a pitch circumferential speed of 1 mZS. The lubricating oil used was a rare resin-based grease. The groove 2, a circular arc cross sectional shape, and a width 0. 2 mm, depth 0 7 mm, the groove volume 0. 0 5 mm 3.
このグラフでは、 縦軸の温度をとり横軸に歯車の破断に至るまでの総 回転数をとつたものである。溝 2を歯末側に 1本設けた場合に 5 0 前 後の温度域を長期に保持して耐久性能が高くなつていることが理解さ れる。  In this graph, the vertical axis shows the temperature, and the horizontal axis shows the total number of revolutions before the gear breaks. It can be understood that when one groove 2 is provided on the tooth end side, the temperature range around 50 is maintained for a long time, and the durability performance is enhanced.
以上、 図示した各例の外に、 溝 2を歯面 1の歯元側にのみ設けること も可能である。  As described above, in addition to the illustrated examples, the groove 2 may be provided only on the root side of the tooth surface 1.
さらに、 前述の各例を適宜組合わせることも可能である。 産業上の利用可能性  Further, the above-described examples can be appropriately combined. Industrial applicability
本発明は、 はすば歯車， ウォーム歯車等にも適用することが可能であ る。  The present invention can be applied to helical gears, worm gears, and the like.

Claims

請 求 の 範 囲 The scope of the claims
1 . 歯面に潤滑油を溜める溝が設けられた歯車において、 溝は歯面の嚙 合い有効面の歯末側の端部付近に位置され歯幅の全幅に配設されてい ることを特徴とする歯車。 1. In a gear provided with a groove for storing lubricating oil on the tooth surface, the groove is located near the end of the tooth flank side of the mating effective surface and is disposed over the entire width of the tooth width. And gears.
2 . 歯面に潤滑油を溜める溝が設けられた歯車において、 溝は歯面の嚙 合い有効面の歯元側の端部付近に位置され歯幅の全幅に配設されてい ることを特徴とする歯車。  2. In a gear provided with a groove for storing lubrication oil on the tooth surface, the groove is located near the root end of the mating effective surface and is disposed over the entire width of the tooth width. And gears.
3 . 請求の範囲 1または 2の歯車において、 溝は歯幅の全幅に連続した 窪みとして直線状に配設されていることを特徴とする歯車。  3. The gear according to claim 1 or 2, wherein the grooves are linearly arranged as depressions continuous with the entire tooth width.
4 . 請求の範囲 1または 2の歯車において、 溝は歯幅の全幅に間欠した 窪みとして直線状に配設されていることを特徴とする歯車。  4. The gear according to claim 1 or 2, wherein the groove is linearly arranged as a recess intermittently over the entire tooth width.
5 . 請求の範囲 3または 4の歯車において、 溝は複数列に並列されてい ることを特徴とする歯車。  5. The gear according to claim 3, wherein the grooves are arranged in a plurality of rows.
6 . 請求の範囲 5の歯車において、 溝の各列の窪みはピッチ円に向けて 潤滑油を溜める量が順次少なくなるように形成されていることを特徴 とする歯車。 6. The gear according to claim 5, wherein the depressions in each row of the grooves are formed so that the amount of the lubricating oil that accumulates gradually decreases toward the pitch circle.
7 . 請求の範囲 1または 2の歯車において、 溝は歯幅の全幅に散点した 微小な窪みとして帯状に配設されていることを特徴とする歯車。  7. The gear according to claim 1 or 2, wherein the groove is arranged in a strip shape as a minute depression scattered over the entire width of the tooth width.
8 . 請求の範囲 7の歯車において、 溝の窪みはピッチ円に向けて潤滑油 を溜める量が順次少なくなるように形成されていることを特徴とする 歯早。 8. The gear according to claim 7, wherein the recess of the groove is formed so that the amount of lubricating oil that accumulates gradually decreases toward the pitch circle.
9 . 請求の範囲 1〜 8のいずれかの歯車において、 形成材料は嚙合いで 歯面の嚙合い有効面の歯末側の端部付近に位置された溝を僅かに変形 させる弾性を有していることを特徴とする歯車。  9. The gear according to any one of claims 1 to 8, wherein the forming material has an elasticity to slightly deform a groove located near the end of the toothed surface of the toothed surface. A gear that is characterized by:
PCT/JP2003/011024 2002-08-29 2003-08-29 Gear WO2004020876A1 (en)

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EP2508778A3 (en) * 2011-03-28 2015-06-24 Robert Bosch GmbH Gear wheel and gear-drive unit
CN102889362A (en) * 2012-10-31 2013-01-23 浙江大学 Gear with surface texture tooth surfaces
CN104179935A (en) * 2013-05-27 2014-12-03 内蒙古欧意德发动机有限公司 Gear and gear transmission device
CN103240342A (en) * 2013-05-28 2013-08-14 昆山众信精密模具标准件有限公司 Novel gear device for concave and convex mold
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CN103291884A (en) * 2013-06-19 2013-09-11 孙维 Improved structure planetary gear

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