JP2007002885A - Differential gear - Google Patents

Differential gear Download PDF

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JP2007002885A
JP2007002885A JP2005181493A JP2005181493A JP2007002885A JP 2007002885 A JP2007002885 A JP 2007002885A JP 2005181493 A JP2005181493 A JP 2005181493A JP 2005181493 A JP2005181493 A JP 2005181493A JP 2007002885 A JP2007002885 A JP 2007002885A
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gear
differential case
spherical
differential
back surface
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Hiroaki Sato
博昭 佐藤
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Aisin Takaoka Co Ltd
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Aisin Takaoka Co Ltd
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    • 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
    • F16H57/0427—Guidance of lubricant on rotary parts, e.g. using baffles for collecting lubricant by centrifugal force
    • 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
    • F16H57/0463—Grease lubrication; Drop-feed lubrication
    • 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
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0483—Axle or inter-axle differentials

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a differential gear less causing machining burrs in finish machining the surfaces of a recessed part or a groove for securing lubrication during slidable movement formed in the rear face of a gear or a seat face of the inside wall part of a differential case in contact with the rear face and providing excellent retainability and feeding property of lubricating oil in use. <P>SOLUTION: This differential gear comprises a differential case and a pinion gear supported, in a contact state, on the spherical seat face 15 of the inside wall part of the differential case. A plurality of grooves are formed in the spherical rear face of the pinion gear. A plurality of recessed parts 16 are formed in the spherical seat face 15 in contact with the spherical rear face of the pinion gear. Each recessed part 16 is formed in a conical shape with a conical surface-shaped inner peripheral surface 17. The tilt angle θ1 of the conical surface-shaped inner peripheral surface 17 relative to the centerline Q of the recessed part 16 is set to 45 to 60°. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、自動車の駆動系などの動力伝達機構に使用される差動装置（ディフェレンシャルギア）に関するものである。   The present invention relates to a differential gear (differential gear) used in a power transmission mechanism such as a driving system of an automobile.

例えば自動車の駆動系には、左右の駆動輪あるいは前後の駆動車軸の回転数差を吸収して円滑な転がり走行を実現するための差動装置が設けられている。一般に差動装置は、ギア収納室が内部に区画された差動ケース、並びに、その差動ケースのギア収納室内に組み込まれる一対のピニオンギア及び一対のサイドギアを具備する。ピニオンギアは、例えば球面状の背面を持った傘歯車として構成される。他方、差動ケースのギア収納室には、ピニオンギアの球面状背面に対応する球面状の内壁面が形成される。現在製品化されている大多数の差動装置では、差動ケースのギア収納室の球面状内壁面とピニオンギアの球面状背面との間に球面薄板状のピニオンギアワッシャーを介在させた状態で、差動ケースの球面状内壁面に対しピニオンギアを摺動可能に支持している。球面薄板状のピニオンギアワッシャーは、外部から供給される潤滑オイルを巻き込んで、差動ケースの球面状内壁面とピニオンギアの球面状背面との間の摺動性及び潤滑性を確保する働きをする（ピニオンギアワッシャーの例としては例えば特許文献１参照）。   For example, a drive system of an automobile is provided with a differential device for realizing smooth rolling running by absorbing a difference in rotational speed between left and right drive wheels or front and rear drive axles. Generally, the differential device includes a differential case having a gear housing chamber defined therein, and a pair of pinion gears and a pair of side gears incorporated in the gear housing chamber of the differential case. The pinion gear is configured as a bevel gear having a spherical back surface, for example. On the other hand, a spherical inner wall surface corresponding to the spherical back surface of the pinion gear is formed in the gear housing chamber of the differential case. In most of the differential devices that are currently commercialized, a spherical thin pinion gear washer is interposed between the spherical inner wall surface of the gear housing chamber of the differential case and the spherical rear surface of the pinion gear. The pinion gear is slidably supported on the spherical inner wall surface of the differential case. The spherical thin pinion gear washer entrains lubrication oil supplied from the outside, and serves to ensure slidability and lubricity between the spherical inner wall surface of the differential case and the spherical rear surface of the pinion gear. (For example, see Patent Document 1 as an example of a pinion gear washer).

ただし、ピニオンギアワッシャーを必要とすることで部品点数が多くなるという欠点がある。また、多数の部品の組み付け作業性を配慮すると、差動ケース自体の小型化が難しいという問題が生ずる。かかる事情を考慮して、ワッシャー類を必要としない設計が提案されている。例えば特許文献２の差動制限装置では、ピニオンギアワッシャーを省く代わりに、ピニオンギアの球面状背面に螺旋状の油溝（３Ａ，４Ａ）を刻設し、この油溝を循環する潤滑油により部材間の焼き付きを防止している。   However, there is a disadvantage that the number of parts increases due to the need for the pinion gear washer. Further, when considering the workability of assembling a large number of parts, there arises a problem that it is difficult to downsize the differential case itself. In consideration of such circumstances, a design that does not require washers has been proposed. For example, in the differential limiting device of Patent Document 2, instead of omitting the pinion gear washer, a helical oil groove (3A, 4A) is formed on the spherical back surface of the pinion gear, and the lubricating oil circulating through the oil groove is used. Burn-in between members is prevented.

しかしながら、ピニオンギアの球面状背面にあっては、油溝の形成後において当該背面の球面精度を確保するために球面仕上げ加工を施す必要が生じる。その際、油溝の形成状況によっては、溝の開口縁に加工バリ（具体的には「返りバリ」）が生じるという問題がある。溝の開口縁に加工バリが残ったままだと、差動ケースの球面状内壁面とピニオンギアの球面状背面との円滑な摺動が妨げられるので、加工バリを除去するために更に追加加工が必要になるというジレンマがある。   However, in the spherical rear surface of the pinion gear, it is necessary to perform spherical finishing to ensure the spherical accuracy of the rear surface after the oil groove is formed. At that time, depending on the formation state of the oil groove, there is a problem that a processing burr (specifically, a “return burr”) is generated at the opening edge of the groove. If the processing burr remains at the opening edge of the groove, smooth sliding between the spherical inner wall surface of the differential case and the spherical back surface of the pinion gear is hindered, so additional processing is required to remove the processing burr. There is a dilemma that is necessary.

特開平９−１８４５６１号公報（デフピニオンギアワッシャ２０）Japanese Patent Laid-Open No. 9-184561 (Deppinion Gear Washer 20) 特開平９−４９５５７号公報（第０００８段落、第００１９段落）JP-A-9-49557 (paragraphs 0008 and 0019)

本発明の目的は、ギアの背面又はその背面が接触する差動ケース内壁部の座面に設けられた摺動時の潤滑確保のための凹部又は溝につき、面の仕上げ加工時には加工バリが生じ難く、且つ、使用時には潤滑油の保持性及び供給性が良好である差動装置を提供することにある。   An object of the present invention is to provide a processing burr at the time of finishing the surface of the recess or groove for ensuring lubrication during sliding provided on the back surface of the gear or the seat surface of the inner wall portion of the differential case with which the back surface contacts. It is an object of the present invention to provide a differential device that is difficult and has good retention and supply of lubricating oil when used.

請求項１の発明は、差動ケース及びその内部に組み込まれるギアを備え、差動ケース内壁部の座面にギアの背面を接触させた状態で差動ケース内にギアを回動可能に支持する差動装置において、前記ギアの背面及びその背面が接触する差動ケースの座面のうちの少なくとも一方には、円錐面状の内周面を有する略すり鉢形状の凹部が設けられており、その凹部の中心線（Ｑ）に対する前記円錐面状内周面の傾斜角度（θ１）が４５°以上６０°以下に設定されていることを特徴とする差動装置である。   The invention of claim 1 includes a differential case and a gear incorporated therein, and the gear is rotatably supported in the differential case with the back surface of the gear in contact with the seating surface of the inner wall portion of the differential case. In the differential device, at least one of the back surface of the gear and the seat surface of the differential case with which the back surface is in contact is provided with a substantially mortar-shaped recess having a conical inner peripheral surface, The differential device is characterized in that an inclination angle (θ1) of the conical inner peripheral surface with respect to the center line (Q) of the concave portion is set to 45 ° or more and 60 ° or less.

なお、請求項１中の「略すり鉢形状」とは、底が一点に収束するようなすり鉢形状のほかに、所定面積の底面を持ったすり鉢形状（即ち円錐台を上下逆にしたような凹形状）をも含む意味である。   In addition, the “substantially mortar shape” in claim 1 is a mortar shape having a bottom surface of a predetermined area in addition to a mortar shape whose bottom converges to one point (that is, a concave shape in which a truncated cone is turned upside down. Shape).

請求項２の発明は、差動ケース及びその内部に組み込まれるギアを備え、差動ケース内壁部の座面にギアの背面を接触させた状態で差動ケース内にギアを回動可能に支持する差動装置において、前記ギアの背面及びその背面が接触する差動ケースの座面のうちの少なくとも一方には、左右二つの傾斜した溝形成面を有する略Ｖ字断面形状の溝が設けられており、その溝を左右に二分割する中心面（Ｐ）に対する前記各溝形成面の傾斜角度（θ２）が４５°以上６０°以下に設定されていることを特徴とする差動装置である。   The invention of claim 2 includes a differential case and a gear incorporated therein, and the gear is rotatably supported in the differential case with the back surface of the gear in contact with the seating surface of the inner wall portion of the differential case. In the differential device, at least one of the back surface of the gear and the seat surface of the differential case with which the back surface contacts is provided with a groove having a substantially V-shaped cross section having two inclined right and left groove forming surfaces. A differential device characterized in that an inclination angle (θ2) of each groove forming surface with respect to a central plane (P) that divides the groove into left and right parts is set to 45 ° or more and 60 ° or less. .

なお、請求項２中の「略Ｖ字断面形状」とは、底が鋭角的なＶ字断面形状のほかに、所定長の底辺を持ったＶ字断面形状（即ち台形を上下逆にしたような断面形状）をも含む意味である。   The “substantially V-shaped cross-sectional shape” in claim 2 is a V-shaped cross-sectional shape having a base of a predetermined length in addition to an acute V-shaped cross-sectional shape (that is, a trapezoid is inverted upside down). Mean cross-sectional shape).

請求項１又は２に記載の差動装置において、前記ギアは球面状の背面を持ったピニオンギアであり、そのピニオンギアの球面状背面が接触する差動ケースの座面も球面状をなしていること（請求項３）は好ましい。   The differential gear according to claim 1 or 2, wherein the gear is a pinion gear having a spherical back surface, and the seating surface of the differential case with which the spherical back surface of the pinion gear contacts also has a spherical shape. (Claim 3) is preferable.

［作用］
本発明では、ギアの背面及びその背面が接触する差動ケースの座面のうちの少なくとも一方に設けられた略すり鉢形状の凹部（又は略Ｖ字断面形状の溝）において、略すり鉢形状の凹部を構成する円錐面状内周面の傾斜角度θ１（又は略Ｖ字断面形状の溝を構成する溝形成面の傾斜角度θ２）を４５°以上６０°以下に設定している。このため、ギア背面又は座面の仕上げ加工時において凹部（又は溝）の開口縁で加工バリが発生する事態を抑制することと、凹部（又は溝）が潤滑油を保持し供給する機能とを両立させることができる。すなわち、傾斜角度θ１（又はθ２）が４５°未満になると、凹部（又は溝）の開口縁において加工バリが生じ易くなる。他方、傾斜角度θ１（又はθ２）が６０°を超えると、凹部（又は溝）の深さが非常に浅くなり、その内部に潤滑油を保持する機能や潤滑油を供給する機能が損なわれる。なお、前記ギアが球面状の背面を持ったピニオンギアであり、そのピニオンギアの球面状背面が接触する差動ケースの座面も球面状をなす場合には特に、本発明の有用性は高い。 [Action]
In the present invention, in a substantially mortar-shaped recess (or a groove having a substantially V-shaped cross section) provided in at least one of the back surface of the gear and the seat surface of the differential case with which the back surface contacts, a substantially mortar-shaped recess Is set to 45 ° or more and 60 ° or less. (Inclination angle θ1 of the conical inner circumferential surface (or inclination angle θ2 of a groove forming surface forming a groove having a substantially V-shaped cross section)). For this reason, at the time of finishing the back surface of the gear or the seating surface, it is possible to suppress the occurrence of processing burr at the opening edge of the recess (or groove), and the function that the recess (or groove) holds and supplies the lubricating oil. Both can be achieved. That is, when the inclination angle θ1 (or θ2) is less than 45 °, processing burrs are likely to occur at the opening edge of the recess (or groove). On the other hand, when the inclination angle θ1 (or θ2) exceeds 60 °, the depth of the concave portion (or groove) becomes very shallow, and the function of holding the lubricating oil therein and the function of supplying the lubricating oil are impaired. The present invention is particularly useful when the gear is a pinion gear having a spherical back surface, and the seating surface of the differential case with which the spherical back surface of the pinion gear contacts also has a spherical shape. .

本発明によれば、差動ケース及びその内部に組み込まれるギアを備え、差動ケース内壁部の座面にギアの背面を接触させた状態で差動ケース内にギアを回動可能に支持すると共に、ギアの背面及びその背面が接触する差動ケースの座面のうちの少なくとも一方に、摺動時の潤滑確保のための凹部又は溝を備えた差動装置において、その凹部又は溝につき、ギア背面又は座面の仕上げ加工時には加工バリを生じ難くする一方で、使用時には潤滑油の保持性及び供給性を良好にすることができる。   According to the present invention, the differential case and the gear incorporated therein are provided, and the gear is rotatably supported in the differential case in a state where the back surface of the gear is in contact with the seating surface of the differential case inner wall. And at least one of the back surface of the gear and the seat surface of the differential case with which the back surface is in contact with a recess or groove for ensuring lubrication at the time of sliding, in the recess or groove, While it is difficult to produce a processing burr at the time of finishing the gear back or seating surface, it is possible to improve the retention and supply of the lubricating oil during use.

本発明を自動車の駆動系に装備される差動装置に具体化した一実施形態を図面を参照しつつ説明する。図１（Ａ）に示すように、自動車用の差動装置は少なくとも、差動ケース１、一対のピニオンギア２及び一対のサイドギア３を備える。この差動装置は、デフキャリア（図示略）内に回転軸線Ｃを中心として回転可能に支持されるものである。   An embodiment in which the present invention is embodied in a differential gear equipped in a drive system of an automobile will be described with reference to the drawings. As shown in FIG. 1A, the differential for an automobile includes at least a differential case 1, a pair of pinion gears 2, and a pair of side gears 3. This differential device is supported in a differential carrier (not shown) so as to be rotatable about a rotation axis C.

図１（Ａ）及び（Ｂ）に示すように、差動ケース１は、その内部に複数のギア類（２，３）を組み込むためのギア収納室１０を区画するケース体として構成されている。差動ケース１の外周部には、回転軸線Ｃを取り囲むようにフランジ部１１が設けられている。このフランジ部１１には、エンジンの駆動力を当該差動ケース１に伝達するための傘歯状のリングギア１２（仮想線で示す）がボルト等の締結具によって固定される。   As shown in FIGS. 1A and 1B, the differential case 1 is configured as a case body that defines a gear storage chamber 10 for incorporating a plurality of gears (2, 3) therein. . A flange portion 11 is provided on the outer peripheral portion of the differential case 1 so as to surround the rotation axis C. A bevel tooth ring gear 12 (shown by an imaginary line) for transmitting the driving force of the engine to the differential case 1 is fixed to the flange portion 11 by a fastener such as a bolt.

差動ケース１のギア収納室１０の左右の内壁部にはそれぞれ、左右一対のサイドギア３を回転軸線Ｃ回りで回転可能に支持するための台座部（１３，１４）が形成されている。この台座部は、少なくとも平面状の座面１３及び円筒状の座面１４から構成されている。他方、差動ケース１のギア収納室１０の上下の内壁部にはそれぞれ、上下一対のピニオンギア２を回転可能に支持するための球面状の座面１５が形成されている。各座面１５の球面形状は、その座面１５に接触するピニオンギア２の背面２３の球面形状に対応しており、ピニオンギア２の球面状背面２３が差動ケース内壁の球面状座面１５に接触（着座）することにより、各ピニオンギア２が差動ケース１内で位置決めされる。   The left and right inner walls of the gear housing chamber 10 of the differential case 1 are formed with pedestals (13, 14) for supporting the pair of left and right side gears 3 so as to be rotatable about the rotation axis C, respectively. The pedestal is composed of at least a planar seat surface 13 and a cylindrical seat surface 14. On the other hand, spherical seating surfaces 15 for rotatably supporting the pair of upper and lower pinion gears 2 are formed on the upper and lower inner walls of the gear housing chamber 10 of the differential case 1. The spherical shape of each seating surface 15 corresponds to the spherical shape of the back surface 23 of the pinion gear 2 that contacts the seating surface 15, and the spherical back surface 23 of the pinion gear 2 is the spherical seating surface 15 of the inner wall of the differential case. The pinion gears 2 are positioned in the differential case 1 by contacting (sitting) with each other.

図２（Ａ）は、差動ケース１のギア収納室１０の中心から各球面状座面１５を見た状態を示す（図１（Ｂ）の「視方向」矢印参照）。 図２（Ａ）に示すように、球面状座面１５には、複数の凹部１６が形成されている。図２（Ｂ）及び（Ｃ）は、個々の凹部１６の正面及びＡ−Ａ線断面（径方向断面）を示す。これらの図面に示すように、球面状座面１５の凹部１６は、すり鉢形状（つまり逆円錐形状）をなしており、そのすり鉢形状の凹部１６は、円錐面状の内周面１７を有している。そして、この円錐面状の内周面１７は、凹部１６の中心線Ｑ（この中心線Ｑは球面状座面１５の球の半径方向に延びる）に対して所定の傾斜角度θ１で傾斜している。この傾斜角度θ１は４５°〜６０°に設定される。   FIG. 2A shows a state in which each spherical seating surface 15 is viewed from the center of the gear housing chamber 10 of the differential case 1 (see the “viewing direction” arrow in FIG. 1B). As shown in FIG. 2A, the spherical seat surface 15 has a plurality of recesses 16 formed therein. 2B and 2C show the front and individual AA line cross sections (radial cross sections) of the individual recesses 16. As shown in these drawings, the concave portion 16 of the spherical seating surface 15 has a mortar shape (that is, an inverted conical shape), and the mortar-shaped concave portion 16 has a conical inner peripheral surface 17. ing. The conical inner peripheral surface 17 is inclined at a predetermined inclination angle θ1 with respect to the center line Q of the recess 16 (the center line Q extends in the radial direction of the sphere of the spherical seat surface 15). Yes. This inclination angle θ1 is set to 45 ° to 60 °.

なお、図１（Ｂ）に示すように、差動ケース１には、ギア収納室１０のほかに、シャフトを垂直方向に通すためのシャフト孔１８と、ピンを水平方向に通すためのピン孔１９とが形成されている。   As shown in FIG. 1B, in addition to the gear housing chamber 10, the differential case 1 includes a shaft hole 18 for passing the shaft in the vertical direction and a pin hole for passing the pin in the horizontal direction. 19 is formed.

図３（Ａ）及び（Ｂ）に示すように、ピニオンギア２は、その中心を貫通する中心孔２１を有する傘歯車として構成されている。ピニオンギア２は、同じく傘歯車として構成されたサイドギア３の歯と噛合可能な複数の歯２２を備えている。ピニオンギア２の背面２３は、前記差動ケース１の座面１５の球面形状に対応する球面状に形成されている。そして、各ピニオンギア２の球面状背面２３には、複数条の溝２４（本例では４条）がギアの半径方向に沿って直線的に延びるように刻設されている。特に図３（Ｂ）及び（Ｃ）に示すように、ピニオンギア背面２３の溝２４はほぼＶ字状の横断面形状をなし、左右二つの傾斜した溝形成面２４ａ，２４ｂを有している。そして、これらの傾斜した溝形成面２４ａ，２４ｂは、その溝２４を左右に二分割する中心面Ｐに対して所定の傾斜角度θ２で傾斜している。この傾斜角度θ２は４５°〜６０°に設定される。   As shown in FIGS. 3A and 3B, the pinion gear 2 is configured as a bevel gear having a center hole 21 penetrating the center. The pinion gear 2 includes a plurality of teeth 22 that can mesh with the teeth of the side gear 3 that is also configured as a bevel gear. The back surface 23 of the pinion gear 2 is formed in a spherical shape corresponding to the spherical shape of the seating surface 15 of the differential case 1. A plurality of grooves 24 (four in this example) are engraved on the spherical rear surface 23 of each pinion gear 2 so as to extend linearly along the radial direction of the gear. In particular, as shown in FIGS. 3B and 3C, the groove 24 on the pinion gear back surface 23 has a substantially V-shaped cross-sectional shape, and has two inclined right and left groove forming surfaces 24a and 24b. . The inclined groove forming surfaces 24a and 24b are inclined at a predetermined inclination angle θ2 with respect to the center plane P that divides the groove 24 into left and right parts. This inclination angle θ2 is set to 45 ° to 60 °.

図１（Ａ）に示すように、差動ケース１の左右の台座部（１３，１４）に対して左右一対のサイドギア３を当接させると共に、差動ケース１の上下の球面状座面１５に対して上下一対のピニオンギア２を当接させ、且つ、隣り合うサイドギア３とピニオンギア２とを互い噛合させる。そして、上下のピニオンギア２の中心孔２１及び差動ケース１のシャフト孔１８を貫通するように一本のピニオンギアシャフト４を垂直に通すと共に、該ピニオンギアシャフト４の上端部を水平に貫通するように一本の固定ピン５を差動ケースのピン孔１９内に装着する。このようにして、差動ケース１内にピニオンギア２及びサイドギア３が組み込まれた差動装置を組み立てている。なお、各サイドギア３はその中心を貫通する中心孔３１を有しており、その中心孔３１の内周部には、車輪のアクスル軸とスプライン嵌合させるための複数のスプラインキー（図示略）が形成されている。   As shown in FIG. 1A, a pair of left and right side gears 3 are brought into contact with the left and right pedestals (13, 14) of the differential case 1, and the upper and lower spherical seating surfaces 15 of the differential case 1 are contacted. A pair of upper and lower pinion gears 2 are brought into contact with each other, and adjacent side gears 3 and pinion gears 2 are engaged with each other. Then, the single pinion gear shaft 4 is vertically passed through the center hole 21 of the upper and lower pinion gears 2 and the shaft hole 18 of the differential case 1 and the upper end portion of the pinion gear shaft 4 is horizontally penetrated. As described above, one fixing pin 5 is mounted in the pin hole 19 of the differential case. In this manner, the differential device in which the pinion gear 2 and the side gear 3 are incorporated in the differential case 1 is assembled. Each side gear 3 has a center hole 31 penetrating through the center thereof, and a plurality of spline keys (not shown) for spline fitting with the axle shaft of the wheel on the inner peripheral portion of the center hole 31. Is formed.

かかる差動装置は、リングギア１２を介して伝達されるエンジンの駆動力に基づき、デフキャリア（図示略）内において回転軸線Ｃを中心として回転する。その際、デフキャリア内に貯留されている潤滑油が回転する差動ケース１によって掻き回されて飛散し、差動装置の各部に供給される。その際、差動ケース１の各台座部（１３，１４）とそれに接触するサイドギア３の背面との間や、差動ケース１の各球面状座面１５とそれに接触するピニオンギア２の球面状背面２３との間にも、飛散した潤滑油が供給される。   Such a differential device rotates around a rotation axis C in a differential carrier (not shown) based on the driving force of the engine transmitted through the ring gear 12. At that time, the lubricating oil stored in the differential carrier is stirred and scattered by the rotating differential case 1 and supplied to each part of the differential device. At that time, each pedestal portion (13, 14) of the differential case 1 and the back surface of the side gear 3 in contact therewith, or each spherical seat surface 15 of the differential case 1 and the spherical surface of the pinion gear 2 in contact therewith. The scattered lubricating oil is also supplied to the back surface 23.

差動ケース１の球面状座面１５とピニオンギア２の球面状背面２３との間に供給された潤滑油は、球面状座面１５側の凹部１６やピニオンギア背面２３の溝２４に一時的に蓄えられる。特にピニオンギア背面２３の半径方向に延びる各溝２４は、ピニオンギア２の外周部から中心孔２１に向かって又はその逆の向きに潤滑油を導くので、差動ケース１の球面状座面１５とピニオンギア２の球面状背面２３とが接する領域にも、潤滑油の供給・排出による油の循環が生じ得る。従って、差動ケース１とピニオンギア２との間の焼付きや異常摩耗を防止しつつ、両者の円滑な相対摺動（相対回動）が確保される。   Lubricating oil supplied between the spherical seating surface 15 of the differential case 1 and the spherical back surface 23 of the pinion gear 2 temporarily enters the recess 16 on the spherical seating surface 15 side or the groove 24 on the pinion gear back surface 23. Stored in In particular, each groove 24 extending in the radial direction of the pinion gear back surface 23 guides the lubricating oil from the outer peripheral portion of the pinion gear 2 toward the center hole 21 or vice versa, so that the spherical seating surface 15 of the differential case 1 is provided. In the region where the pinion gear 2 and the spherical back surface 23 are in contact with each other, oil circulation due to supply / discharge of the lubricating oil may occur. Therefore, while preventing seizure and abnormal wear between the differential case 1 and the pinion gear 2, smooth relative sliding (relative rotation) between the two is ensured.

本実施形態では、差動ケース１の球面状座面１５に設けられた各凹部１６の内周面１７の傾斜角度θ１は、凹部の中心線Ｑに対して４５°以上となるように設定されている。このため、例えば球面状座面１５の球面精度を確保するための球面仕上げ加工（例えば研磨加工）を行った場合でも、既設の凹部１６の開口縁において「返りバリ」が発生し難く、凹部１６の存在が球面仕上げの阻害又は障害原因となることがない。従って本実施形態によれば、摺動時の潤滑確保のための凹部１６を備えた球面状座面１５の球面精度を向上させることができる。   In the present embodiment, the inclination angle θ1 of the inner peripheral surface 17 of each recess 16 provided on the spherical seating surface 15 of the differential case 1 is set to be 45 ° or more with respect to the center line Q of the recess. ing. For this reason, for example, even when a spherical finishing process (for example, a polishing process) for ensuring the spherical accuracy of the spherical seating surface 15 is performed, a “return burr” is unlikely to occur at the opening edge of the existing recess 16, and the recess 16 The presence of the surface does not interfere with or obstruct the spherical finish. Therefore, according to the present embodiment, it is possible to improve the spherical accuracy of the spherical seating surface 15 provided with the recess 16 for ensuring lubrication during sliding.

同様に、ピニオンギア２の球面状背面２３に設けられた溝２４の各溝形成面２４ａ，２４ｂの傾斜角度θ２は、溝の中心面Ｐに対して４５°以上となるように設定されている。このため、例えば球面状背面２３の球面精度を確保するための球面仕上げ加工（例えば研磨加工）を行った場合でも、既設の溝２４の開口縁において「返りバリ」が発生し難く、溝２４の存在が球面仕上げの阻害又は障害原因となることがない。従って本実施形態によれば、摺動時の潤滑確保のための溝２４を備えたピニオンギア２の球面状背面２３の球面精度を向上させることができる。   Similarly, the inclination angle θ2 of each groove forming surface 24a, 24b of the groove 24 provided on the spherical back surface 23 of the pinion gear 2 is set to be 45 ° or more with respect to the center plane P of the groove. . For this reason, for example, even when spherical finishing (for example, polishing) for ensuring the spherical accuracy of the spherical back surface 23 is performed, “return burr” hardly occurs at the opening edge of the existing groove 24. Presence does not cause hindrance or obstruction of spherical finish. Therefore, according to the present embodiment, it is possible to improve the spherical accuracy of the spherical back surface 23 of the pinion gear 2 provided with the grooves 24 for ensuring lubrication during sliding.

他方、凹部１６の内周面１７の傾斜角度θ１及び溝２４の各溝形成面２４ａ，２４ｂの傾斜角度θ２ともに、凹部の中心線Ｑ又は溝の中心面Ｐに対して６０°以下となるように設定されている。このため、凹部１６及び溝２４の深さは油保持等のために最低限必要な程度確保されており、凹部１６及び溝２４が潤滑油を保持する機能や、潤滑油を凹部１６又は溝２４内からその周辺に供給する機能が損なわれることはない。即ち、本実施形態の傾斜角度θ１及びθ２の設定によれば、凹部１６及び溝２４における加工バリの発生抑制と、凹部１６及び溝２４における潤滑油の保持供給機能とを両立させることができる。   On the other hand, both the inclination angle θ1 of the inner peripheral surface 17 of the recess 16 and the inclination angle θ2 of each groove forming surface 24a, 24b of the groove 24 are 60 ° or less with respect to the center line Q of the recess or the center plane P of the groove. Is set to For this reason, the depths of the recesses 16 and the grooves 24 are secured to a minimum necessary level for oil retention and the like, and the functions of the recesses 16 and the grooves 24 to hold the lubricating oil, and the lubricant oil to the recesses 16 and the grooves 24. The function of supplying to the periphery from the inside is not impaired. That is, according to the setting of the inclination angles θ1 and θ2 of the present embodiment, it is possible to achieve both the suppression of processing burr generation in the recess 16 and the groove 24 and the function of holding and supplying the lubricating oil in the recess 16 and the groove 24.

［変更例］上記実施形態では、差動ケース１の球面状座面１５に複数の凹部１６を形成し、ピニオンギア２の背面２３に複数の溝２４を形成したが、球面状座面１５の側に溝を形成し、ピニオンギア背面２３の側に凹部を形成してもよい。また、球面状座面１５及びピニオンギア背面２３の双方に凹部（１６）を形成してもよいし、球面状座面１５及びピニオンギア背面２３の双方に溝（２４）を形成してもよい。あるいは、球面状座面１５及びピニオンギア背面２３のうちの一方にのみ、凹部（１６）又は溝（２４）を形成してもよい。   [Modification] In the above embodiment, the plurality of recesses 16 are formed on the spherical seating surface 15 of the differential case 1 and the plurality of grooves 24 are formed on the back surface 23 of the pinion gear 2. A groove may be formed on the side, and a recess may be formed on the pinion gear back surface 23 side. Further, the concave portion (16) may be formed on both the spherical seat surface 15 and the pinion gear back surface 23, or the groove (24) may be formed on both the spherical seat surface 15 and the pinion gear back surface 23. . Alternatively, the recess (16) or the groove (24) may be formed only on one of the spherical seat surface 15 and the pinion gear back surface 23.

［変更例］上記実施形態では、ピニオンギア背面２３の溝２４を直線的に延びるものとしたが、図４に示すように、溝２４は曲線的に（例えば螺旋状に）延びるものであってもよい。   [Modification] In the above embodiment, the groove 24 on the pinion gear back surface 23 extends linearly. However, as shown in FIG. 4, the groove 24 extends in a curved line (for example, spirally). Also good.

［変更例］上記実施形態では、差動ケース１の球面状座面１５の凹部１６をすり鉢形状としたが、図５（Ａ）に示すように、円錐面状の内周面１７と水平な円形底面２０とから構成される逆円錐台形状の凹部１６’としてもよく、とにかく凹部の中心線Ｑに対する円錐面状の内周面１７の傾斜角度θ１が４５°〜６０°の範囲にあればよい。同様に、上記実施形態では、ピニオンギア２の背面２３の溝２４を横断面Ｖ字形状としたが、図５（Ｂ）に示すように、左右二つの傾斜した溝形成面２４ａ，２４ｂと水平な溝底面２５とから構成される横断面が逆台形状の溝２４’としてもよく、とにかく溝の中心面Ｐに対する各溝形成面２４ａ，２４ｂの傾斜角度θ２が４５°〜６０°の範囲にあればよい。   [Modification] In the above embodiment, the concave portion 16 of the spherical seating surface 15 of the differential case 1 has a mortar shape. However, as shown in FIG. It may be an inverted frustoconical concave portion 16 ′ composed of a circular bottom surface 20, and anyway, if the inclination angle θ1 of the conical inner peripheral surface 17 with respect to the center line Q of the concave portion is in the range of 45 ° to 60 °. Good. Similarly, in the above embodiment, the groove 24 on the back surface 23 of the pinion gear 2 has a V-shaped cross section, but as shown in FIG. The groove 24 'may have an inverted trapezoidal cross section composed of the groove bottom surface 25, and the inclination angle θ2 of each groove forming surface 24a, 24b with respect to the groove center plane P is in the range of 45 ° to 60 °. I just need it.

［変更例］サイドギア３についても前記ピニオンギア２と同様に構成してもよい。すなわち、差動ケース１の台座部（１３，１４）を構成する平面状の座面１３又は円筒状の座面１４及びその座面に接触するサイドギア３の背面のうちの少なくとも一方に、前記と同様の凹部１６，１６’又は溝２４，２４’を設けてもよい。   [Modification] The side gear 3 may be configured in the same manner as the pinion gear 2. That is, at least one of the planar seat surface 13 or the cylindrical seat surface 14 constituting the base portion (13, 14) of the differential case 1 and the back surface of the side gear 3 that contacts the seat surface, and Similar recesses 16, 16 'or grooves 24, 24' may be provided.

（Ａ）は差動装置の縦断面図、（Ｂ）は差動ケースの縦断面図。(A) is a longitudinal cross-sectional view of a differential device, (B) is a longitudinal cross-sectional view of a differential case. （Ａ）はピニオンギアが着座する差動ケースの球面状座面の概略正面図、（Ｂ）は球面状座面の凹部の拡大正面図、（Ｃ）は（Ｂ）のＡ−Ａ線での断面図。(A) is a schematic front view of a spherical seating surface of a differential case on which a pinion gear is seated, (B) is an enlarged front view of a concave portion of the spherical seating surface, and (C) is an AA line of (B). FIG. （Ａ）はピニオンギアの径方向断面図、（Ｂ）はピニオンギアの背面図、（Ｃ）はピニオンギア背面の溝の拡大横断面図。(A) is radial direction sectional drawing of a pinion gear, (B) is a rear view of a pinion gear, (C) is an expanded cross-sectional view of the groove | channel of a pinion gear back surface. ピニオンギア背面の溝の変更例を示す図３（Ｂ）相当の背面図。The rear view equivalent to FIG. 3 (B) which shows the example of a change of the groove | channel on the pinion gear back surface. （Ａ）は変更例を示す図２（Ｃ）相当の断面図、（Ｂ）は変更例を示す図３（Ｃ）相当の断面図。FIG. 2A is a cross-sectional view corresponding to FIG. 2C showing a modified example, and FIG. 3B is a cross-sectional view corresponding to FIG.

符号の説明Explanation of symbols

１…差動ケース、２…ピニオンギア、３…サイドギア、１０…ギア収納室、１３…平面状の座面、１４…円筒状の座面、１５…球面状の座面、１６，１６’…凹部、１７…円錐面状の内周面、２３…ピニオンギアの背面、２４，２４’…溝、２４ａ，２４ｂ…溝形成面、Ｃ…回転軸線、Ｐ…溝の中心面、Ｑ…凹部の中心線。   DESCRIPTION OF SYMBOLS 1 ... Differential case, 2 ... Pinion gear, 3 ... Side gear, 10 ... Gear storage chamber, 13 ... Planar seat surface, 14 ... Cylindrical seat surface, 15 ... Spherical seat surface, 16, 16 '... Concave part, 17 ... conical inner peripheral surface, 23 ... back surface of pinion gear, 24, 24 '... groove, 24a, 24b ... groove forming surface, C ... rotational axis, P ... central surface of groove, Q ... concave part Center line.

Claims (3)

差動ケース及びその内部に組み込まれるギアを備え、差動ケース内壁部の座面にギアの背面を接触させた状態で差動ケース内にギアを回動可能に支持する差動装置において、
前記ギアの背面及びその背面が接触する差動ケースの座面のうちの少なくとも一方には、円錐面状の内周面を有する略すり鉢形状の凹部が設けられており、その凹部の中心線（Ｑ）に対する前記円錐面状内周面の傾斜角度（θ１）が４５°以上６０°以下に設定されていることを特徴とする差動装置。 In a differential device comprising a differential case and a gear incorporated in the differential case and rotatably supporting the gear in the differential case in a state where the back surface of the gear is in contact with the seating surface of the inner wall portion of the differential case,
At least one of the back surface of the gear and the seating surface of the differential case with which the back surface contacts is provided with a substantially mortar-shaped recess having a conical inner peripheral surface, and the center line of the recess ( A differential device, wherein an inclination angle (θ1) of the inner circumferential surface of the conical surface with respect to Q) is set to 45 ° or more and 60 ° or less. 差動ケース及びその内部に組み込まれるギアを備え、差動ケース内壁部の座面にギアの背面を接触させた状態で差動ケース内にギアを回動可能に支持する差動装置において、
前記ギアの背面及びその背面が接触する差動ケースの座面のうちの少なくとも一方には、左右二つの傾斜した溝形成面を有する略Ｖ字断面形状の溝が設けられており、その溝を左右に二分割する中心面（Ｐ）に対する前記各溝形成面の傾斜角度（θ２）が４５°以上６０°以下に設定されていることを特徴とする差動装置。 In a differential device comprising a differential case and a gear incorporated in the differential case and rotatably supporting the gear in the differential case in a state where the back surface of the gear is in contact with the seating surface of the inner wall portion of the differential case,
At least one of the back surface of the gear and the seating surface of the differential case with which the back surface is in contact is provided with a groove having a substantially V-shaped cross section having two right and left inclined groove forming surfaces. A differential device characterized in that an inclination angle (θ2) of each groove forming surface with respect to a central plane (P) divided into right and left is set to 45 ° or more and 60 ° or less. 前記ギアは球面状の背面を持ったピニオンギアであり、そのピニオンギアの球面状背面が接触する差動ケースの座面も球面状をなしていることを特徴とする請求項１又は２に記載の差動装置。   3. The gear according to claim 1, wherein the gear is a pinion gear having a spherical back surface, and the seating surface of the differential case with which the spherical back surface of the pinion gear contacts also has a spherical shape. Differential.
JP2005181493A 2005-06-22 2005-06-22 Differential gear Pending JP2007002885A (en)

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US10166318B2 (en) 2015-02-12 2019-01-01 Tc1 Llc System and method for controlling the position of a levitated rotor
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DE102017212274B4 (en) 2016-07-20 2023-11-23 Musashi Seimitsu Industry Co., Ltd. Holder part lubrication structure for a gear member and differential device

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US8827661B2 (en) 2008-06-23 2014-09-09 Thoratec Corporation Blood pump apparatus
US9109601B2 (en) 2008-06-23 2015-08-18 Thoratec Corporation Blood pump apparatus
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US9381285B2 (en) 2009-03-05 2016-07-05 Thoratec Corporation Centrifugal pump apparatus
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US9371826B2 (en) 2013-01-24 2016-06-21 Thoratec Corporation Impeller position compensation using field oriented control
US9709061B2 (en) 2013-01-24 2017-07-18 Tc1 Llc Impeller position compensation using field oriented control
US9556873B2 (en) 2013-02-27 2017-01-31 Tc1 Llc Startup sequence for centrifugal pump with levitated impeller
US10052420B2 (en) 2013-04-30 2018-08-21 Tc1 Llc Heart beat identification and pump speed synchronization
US10980928B2 (en) 2013-04-30 2021-04-20 Tc1 Llc Cardiac pump with speed adapted for ventricle unloading
US9713663B2 (en) 2013-04-30 2017-07-25 Tc1 Llc Cardiac pump with speed adapted for ventricle unloading
US11724094B2 (en) 2013-04-30 2023-08-15 Tc1 Llc Cardiac pump with speed adapted for ventricle unloading
US9623161B2 (en) 2014-08-26 2017-04-18 Tc1 Llc Blood pump and method of suction detection
US10506935B2 (en) 2015-02-11 2019-12-17 Tc1 Llc Heart beat identification and pump speed synchronization
US11712167B2 (en) 2015-02-11 2023-08-01 Tc1 Llc Heart beat identification and pump speed synchronization
US10856748B2 (en) 2015-02-11 2020-12-08 Tc1 Llc Heart beat identification and pump speed synchronization
US11781551B2 (en) 2015-02-12 2023-10-10 Tc1 Llc Alternating pump gaps
US10166318B2 (en) 2015-02-12 2019-01-01 Tc1 Llc System and method for controlling the position of a levitated rotor
US11724097B2 (en) 2015-02-12 2023-08-15 Tc1 Llc System and method for controlling the position of a levitated rotor
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