[go: up one dir, main page]

JP2005081351A - Friction pressure welding member and differential gear equipped with member - Google Patents

Friction pressure welding member and differential gear equipped with member Download PDF

Info

Publication number
JP2005081351A
JP2005081351A JP2003312683A JP2003312683A JP2005081351A JP 2005081351 A JP2005081351 A JP 2005081351A JP 2003312683 A JP2003312683 A JP 2003312683A JP 2003312683 A JP2003312683 A JP 2003312683A JP 2005081351 A JP2005081351 A JP 2005081351A
Authority
JP
Japan
Prior art keywords
differential
friction welding
ring gear
friction
space
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
Application number
JP2003312683A
Other languages
Japanese (ja)
Other versions
JP2005081351A5 (en
Inventor
Koji Obayashi
大林巧治
Keita Taguchi
田口圭太
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin AW Co Ltd
Original Assignee
Aisin AW 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 Aisin AW Co Ltd filed Critical Aisin AW Co Ltd
Priority to JP2003312683A priority Critical patent/JP2005081351A/en
Publication of JP2005081351A publication Critical patent/JP2005081351A/en
Publication of JP2005081351A5 publication Critical patent/JP2005081351A5/ja
Pending legal-status Critical Current

Links

Images

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
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H2048/385—Constructional details of the ring or crown gear
    • 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
    • F16H57/0018—Shaft assemblies for gearings
    • F16H57/0025—Shaft assemblies for gearings with gearing elements rigidly connected to a shaft, e.g. securing gears or pulleys by specially adapted splines, keys or methods

Landscapes

  • Pressure Welding/Diffusion-Bonding (AREA)
  • Retarders (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a friction pressure welding member whereby both man-hours and component items are reduced in number, while obtaining high bonding strength, and also to provide a differential gear equipped with the member. <P>SOLUTION: A differential case 3 is fixed in a state that an annular projection 2d of a differential gear 2 and an annular projection 3d of a differential case 3 are brought into pressure contact with each other in an axial direction under a constant pressure, and then the differential gear 2 is rotated. As a result, friction heat is generated by the rotation at a pressure contact part of the annular projections 2d and 3d and the pressure contact part is heated. By increasing the pressure (upsetting) between the annular projections 2d and 3d, a burr 12 including an oxide or the like on a surface of a heated section is generated. The burr 12 is housed and sealed in spaces 10 and 11. Consequently, newly generated surfaces which appear in the heated contact section of the protrusions 2d and 3d are respectively welded by friction pressure. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、例えば自動車の差動装置等の種々の機械装置における２つの構成部材を接合する摩擦圧接部材およびこれを備えた差動装置の技術分野に関し、特に、繰り返し荷重を受ける部材とこの部材を支持する部材とが互いに接合されて構成される接合部材に好適な摩擦圧接部材およびこれを備えた差動装置の技術分野に関する。   The present invention relates to a friction welding member that joins two components in various mechanical devices such as a differential of an automobile, and a technical field of a differential including the member, and in particular, a member that receives a repeated load and the member. In particular, the present invention relates to a technical field of a friction welding member suitable for a joining member configured by joining members that support each other and a differential device including the same.

自動車等の車両の自動変速機の出力側には、トルクコンバータ及び自動変速装置を介して伝達されるエンジンの動力（トルク）を左右の車輪にそれぞれ各車輪毎に伝達する差動装置が配設されている。この差動装置は、車両の旋回時等の必要時に左右の車輪にそれぞれ対応する左右のドライブシャフトを介して異なる動力を伝達するようになっている（例えば、特許文献１参照）。   On the output side of an automatic transmission of a vehicle such as an automobile, a differential device for transmitting engine power (torque) transmitted via a torque converter and an automatic transmission to left and right wheels for each wheel is provided. Has been. This differential device transmits different power via left and right drive shafts respectively corresponding to left and right wheels when necessary such as when the vehicle is turning (see, for example, Patent Document 1).

ところで、図７に示すようにこのような差動装置１は、自動変速機の出力歯車（不図示）からエンジンの動力が伝達される鋼製のデフリングギヤ２と、このデフリングギヤ２を支持してデフリングギヤ２と一体に回転する鋳鉄製のデフケース３とを備えている。その場合、デフケース３がトランスアクスルハウジング４に回転可能に支持されている。そして、自動変速機の出力がデフリングギヤ２に伝達されると、このデフリングギヤ２が回転するので、デフケース３も回転する。このデフケース３の回転により、ディファレンシャルギヤユニット５もデフケース３と一体に回転する。すると、ベベルギヤからなる左右のサイドギヤ６,７がこれらのギヤ６,７に噛合するディファレンシャルギヤユニット５のベベルギヤ５ａを介して回転する。これにより、左右のドライブシャフト８,９が回転し、これらのドライブシャフト８,９に取り付けられた左右の車輪（不図示）が回転する。   By the way, as shown in FIG. 7, such a differential device 1 supports a steel diff ring gear 2 to which engine power is transmitted from an output gear (not shown) of an automatic transmission, and the diff ring gear 2. And a diff case 3 made of cast iron that rotates integrally with the diff ring gear 2. In that case, the differential case 3 is rotatably supported by the transaxle housing 4. When the output of the automatic transmission is transmitted to the diff ring gear 2, the diff case 3 rotates because the diff ring gear 2 rotates. Due to the rotation of the differential case 3, the differential gear unit 5 also rotates integrally with the differential case 3. Then, the left and right side gears 6, 7 made of bevel gears rotate via the bevel gear 5 a of the differential gear unit 5 that meshes with these gears 6, 7. Thereby, the left and right drive shafts 8 and 9 rotate, and the left and right wheels (not shown) attached to these drive shafts 8 and 9 rotate.

差動装置１におけるデフリングギヤ２とデフケース３との接合は、デフリングギヤ２が繰り返し荷重および衝撃荷重を受けることから高い接合強度（耐疲労強度、耐衝撃強度）が求められる。しかし、鋼と鋳鉄との高強度接合が困難であるため、従来、デフリングギヤ２とデフケース３との高強度接合として、所定数のボルト４によるボルト接合が使用されている。   The differential gear 1 and the differential case 3 in the differential device 1 are required to have high joint strength (fatigue resistance and impact strength) because the differential ring gear 2 receives repeated loads and impact loads. However, since high-strength joining between steel and cast iron is difficult, bolt joining with a predetermined number of bolts 4 is conventionally used as high-strength joining between the diff ring gear 2 and the differential case 3.

また、鋼と鋳鉄との接合として、従来、自動車用ディーゼルエンジンのタイミングギヤ等の高速回転で使用される歯車を、鋼材からなる環状の歯部と鋳鉄からなるボス部とで構成するとともに環状の歯部の内周側にボス部を摩擦圧接することで製造することが提案されている（例えば、特許文献２参照）。   In addition, as a joint between steel and cast iron, a gear conventionally used for high-speed rotation such as a timing gear of an automobile diesel engine is composed of an annular tooth portion made of steel and a boss portion made of cast iron, and an annular shape. It has been proposed to manufacture the boss portion by friction welding the inner peripheral side of the tooth portion (see, for example, Patent Document 2).

一方、車両等に使用される等速ジョイント外輪の製造方法として、等速ジョイント外輪を凹部および短軸部を有するカップ状部と軸部材との２部材で構成し、カップ状部の短軸部と軸部材とを摩擦溶接して等速ジョイント外輪を製造することで、製造時間を短縮するとともに溶接強度を向上することが提案されている（例えば、特許文献３参照）。この特許文献３に開示の摩擦溶接による等速ジョイント外輪の製造方法では、カップ状部の短軸部と軸部材との摩擦溶接の際生じるバリは切削加工により除去している。
特開平９−１０５４４４号公報。 特開２００１−１２４１８０号公報。 特開平１１−７７２２２号公報。 On the other hand, as a method of manufacturing a constant velocity joint outer ring used in a vehicle or the like, the constant velocity joint outer ring is composed of two members, a cup-shaped portion having a recess and a short shaft portion and a shaft member, and the short shaft portion of the cup-shaped portion. It has been proposed that the constant velocity joint outer ring is manufactured by friction welding the shaft and the shaft member, thereby shortening the manufacturing time and improving the welding strength (see, for example, Patent Document 3). In the method for manufacturing a constant velocity joint outer ring by friction welding disclosed in Patent Document 3, burrs generated during friction welding between the short shaft portion of the cup-shaped portion and the shaft member are removed by cutting.
Japanese Patent Laid-Open No. 9-105444. JP 2001-124180 A. Japanese Patent Application Laid-Open No. 11-77222.

しかし、差動装置１におけるデフリングギヤ２とデフケース３との接合として、特許文献１に開示されているようにボルト接合を用いたのでは、差動装置１組みあたり８〜１２本くらいのボルト４が使用されるため、部品点数が多くコスト高となるばかりでなく、重量が重いものとなっている。特に、これらのボルト４には荷重が繰り返しかかることから、その部品機能として耐疲労強度および耐衝撃強度等の高強度が求められるため、更に一層コスト高を招いてしまう。
また、デフリングギヤ２とデフケース３とを手作業でボルト仮付けを行った後、ボルト締め付け機でボルト４を締めつけているため、作業工数が多くかかっている。更に、ボルト４が他の部材との干渉を防止するために、ケースの狭い空間内にこれらのボルト３の占有スペースが必要となっている。 However, if the bolt joint is used as the joint between the differential ring gear 2 and the differential case 3 in the differential device 1 as disclosed in Patent Document 1, about 8 to 12 bolts 4 per differential device pair. Therefore, the number of parts is large and the cost is high, and the weight is heavy. In particular, since loads are repeatedly applied to these bolts 4, high strengths such as fatigue strength and impact strength are required as the function of the parts, which further increases cost.
In addition, since the bolt 4 is tightened with a bolt tightening machine after the differential ring gear 2 and the differential case 3 are temporarily bolted manually, a large number of work steps are required. Furthermore, in order to prevent the bolt 4 from interfering with other members, a space occupied by these bolts 3 is required in a narrow space of the case.

そこで、デフリングギヤ２とデフケース３との接合にボルト接合を用いずに、前述の特許文献２および３に開示されているように摩擦圧接を使用することが考えれる。
しかしながら、特許文献２に開示されている鋼と鋳鉄との摩擦圧接では、この摩擦圧接の際に生じるバリについては考慮されていない。バリが付いている状態で、デフリングギヤとデフケースが回転すると、このバリが他の部材に影響を与えてしまうという問題がある。このため、特許文献３に開示されている摩擦溶接のようにバリを切削加工で取り除くようにすると、バリの切削作業が必要となるばかりでなく、接合強度が低下するおそれがある。しかも、切削加工のための専用の設備が必要となり、更にコスト高となるという問題がある。 Therefore, it is conceivable to use friction welding as disclosed in the above-mentioned Patent Documents 2 and 3 without using bolt joining for joining the differential ring gear 2 and the differential case 3.
However, in the friction welding between steel and cast iron disclosed in Patent Document 2, no consideration is given to burrs generated during this friction welding. When the diff ring gear and the differential case rotate with the burrs attached, there is a problem that the burrs affect other members. For this reason, if the burrs are removed by cutting as in the friction welding disclosed in Patent Document 3, not only the burr cutting operation is required, but also the bonding strength may be reduced. In addition, there is a problem that dedicated equipment for cutting work is required and the cost is further increased.

本発明は、このような事情に鑑みてなされたものであって、その目的は、高接合強度を得つつ、作業工数および部品点数をともに削減できる摩擦圧接部材を提供することである。
本発明の他の目的は、高接合強度を得つつ、占有スペースを低減して他の部材との干渉を防止して確実に動力を伝達することのできる差動装置を提供することである。 This invention is made | formed in view of such a situation, The objective is to provide the friction welding member which can reduce both an operation man-hour and a number of parts, obtaining high joining strength.
Another object of the present invention is to provide a differential device that can reliably transmit power while reducing occupation space and preventing interference with other members while obtaining high joint strength.

前述の課題を解決するために、請求項１の発明の摩擦圧接部材は、互いに摩擦圧接される第１部材と第２部材とからなり、前記第１部材の接合部と前記第２部材の接合部との少なくとも一方に、前記第１部材と前記第２部材が摩擦圧接される際に形成される空所を形成する空所形成部が設けられており、前記摩擦圧接で生じるバリが前記空所に収容されるようにして前記第１部材と前記第２部材が摩擦圧接されていることを特徴としている。   In order to solve the above-mentioned problem, the friction welding member of the invention of claim 1 is composed of a first member and a second member that are friction-welded to each other, and the joining portion of the first member and the second member are joined together. At least one of the first portion and the second portion is provided with a void forming portion that forms a void formed when the first member and the second member are friction-welded. The first member and the second member are friction-welded so as to be housed in a place.

また、請求項２の発明の摩擦圧接部材は、前記第１部材と前記第２部材とが互いに摩擦圧接された状態で一体回転するようになっており、前記第１部材と前記第２部材との少なくとも一方に、前記バリが係合する係合部が前記空所内に位置するようにして設けられていることを特徴としている。   According to a second aspect of the present invention, there is provided the friction welding member according to the second aspect, wherein the first member and the second member are integrally rotated in a state where the first member and the second member are friction-welded with each other. At least one of them is characterized in that an engaging portion with which the burr engages is provided so as to be located in the space.

更に、請求項３の発明の摩擦圧接部材は、前記空所が複数設けられていることを特徴としている。
更に、請求項４の発明の摩擦圧接部材は、前記複数の空所のうち、摩擦圧接される際の部材の回転の回転中心より遠い側の空所の容積が回転中心側の空所の容積より大きく設定されていることを特徴としている。 Furthermore, the friction welding member of the invention of claim 3 is characterized in that a plurality of the voids are provided.
Furthermore, the friction welding member according to the invention of claim 4 is characterized in that, among the plurality of voids, the volume of the void farther from the rotation center of rotation of the member when friction welding is performed is the volume of the void on the rotation center side. It is characterized by being set larger.

更に、請求項５の発明の摩擦圧接部材は、前記第１部材と前記第２部材とが互いに摩擦圧接された状態で一体回転するようになっており、前記第１部材と前記第２部材との少なくとも一方に、前記バリが係合する係合部が前記複数の空所の少なくとも１つに位置するようにして設けられていることを特徴としている。
更に、請求項６の発明は、前記係合部がキー状の突起またはスプラインからなることを特徴としている。 Furthermore, the friction welding member of the invention of claim 5 is configured to rotate integrally in a state where the first member and the second member are friction-welded to each other, and the first member and the second member At least one of them is provided with an engaging portion with which the burr engages in at least one of the plurality of voids.
Further, the invention of claim 6 is characterized in that the engaging portion is formed of a key-shaped protrusion or a spline.

更に、請求項７の発明の差動装置は、少なくともデフリングギヤと、このデフリングギヤを支持しかつデフリングギヤと一体回転するデフケースとを備えている差動装置において、請求項１ないし６のいずれか１の摩擦圧接部材を用い、前記第１部材がデフリングギヤであり、前記第２部材がデフケースであることを特徴としている。   Further, a differential device according to a seventh aspect of the present invention is the differential device according to any one of the first to sixth aspects, comprising at least a differential ring gear and a differential case that supports the differential ring gear and rotates integrally with the differential ring gear. The first member is a diff ring gear, and the second member is a diff case.

このように構成された請求項１ないし５の発明の摩擦圧接部材によれば、第１部材と第２部材とを摩擦圧接した際、生じるバリが空所内に収容される。その場合、空所が閉空間である場合には、このバリは空所内に封じ込められるようになる。これにより、第１部材と第２部材との接合部において、バリが第１部材および第２部材の外部に突出するのを防止できる。特に、第１部材と第２部材とを摩擦圧接における摩擦圧力およびアプセット圧力（摩擦加熱後の加圧力）を調整して接合することで、バリの量を少なくできるとともに、バリの形状を応力集中部が生じない形状にできるので、第１部材と第２部材との接合強度（耐疲労強度および耐衝撃強度）を効果的に向上することができる。   According to the friction welding member of the invention of claims 1 to 5 configured as described above, the burr generated when the first member and the second member are friction welded is accommodated in the void. In that case, when the void is a closed space, the burr is contained in the void. Thereby, it can prevent that a burr | flash protrudes outside the 1st member and the 2nd member in the junction part of the 1st member and the 2nd member. In particular, the amount of burrs can be reduced by joining the first member and the second member by adjusting the friction pressure and the upset pressure (pressure applied after friction heating) in friction welding, and the burr shape is stress concentrated. Therefore, the bonding strength (fatigue resistance and impact strength) between the first member and the second member can be effectively improved.

また、第１部材と第２部材とを摩擦圧接することで、ボルト等の固着具を不要にできる。これにより、部品点数を削減することができるので、コストを低減できるとともに重量を軽減することができる。しかも、ボルト締め等の固着具締結の手作業および機械作業、切削加工等によるバリ取り作業がなくなるので、接合作業の工数を効果的に削減することができ、より一層コストを低減できる。しかも、空所はそれほど高精度に形成する必要がないので、第１および第２部材を鍛造加工あるいは鋳造加工した鍛造肌あるいは鋳造肌のままでよく、仕上げ加工を行う必要はない。したがって、その分、第１および第２部材を容易に製造できるとともに、高精度が必要でない分、製造コストを低減することができる。もちろん、摩擦圧接の当接部は、鍛造肌あるいは鋳造肌のままでは圧接強度および精度に影響が出るため、仕上げ加工が必要である。   Further, the first member and the second member are friction-welded, so that a fixing tool such as a bolt can be eliminated. Thereby, since the number of parts can be reduced, the cost can be reduced and the weight can be reduced. In addition, since there is no deburring work such as bolt fastening and other manual work and machine work, cutting work, etc., the number of man-hours for joining work can be effectively reduced, and the cost can be further reduced. In addition, since the void does not need to be formed with high accuracy, the forged skin or cast skin obtained by forging or casting the first and second members may be used, and there is no need for finishing. Accordingly, the first and second members can be easily manufactured correspondingly, and the manufacturing cost can be reduced because high accuracy is not required. Of course, the contact portion of the friction welding needs to be finished because the forging skin or the casting skin will affect the pressure welding strength and accuracy.

特に、請求項２、５および６の発明によれば、バリが係合部に係合するので、第１および第２部材の間のトルク伝達を確実に行うことができる。
また、請求項４の発明によれば、部材の回転の回転中心より遠い側の空所の容積を回転中心側の空所の容積より大きく設定しているので、周速が高くて発熱量が多くしかもバリ量が多い、部材の回転中心より遠い側部分のバリを、効率よく空所に封じ込めることができる。 In particular, according to the inventions of claims 2, 5 and 6, since the burr engages with the engaging portion, torque transmission between the first and second members can be reliably performed.
According to the invention of claim 4, since the volume of the space far from the rotation center of the rotation of the member is set larger than the volume of the space on the rotation center side, the peripheral speed is high and the heat generation amount is high. The burr on the side far from the rotation center of the member, which has a large amount of burr, can be efficiently contained in the void.

更に、請求項７の発明の差動装置によれば、請求項１ないし６の発明の摩擦圧接部材を用いているので、前述の請求項１ないし６の発明の効果を得ることができる。また、デフリングギヤとデフケースとを摩擦圧接した際、生じるバリが空所内に封じ込められることにより、デフリングギヤとデフケースとの接合部において、バリが外部に突出するのを防止できる。したがって、差動装置のトランスアクスルハウジング内の他の構成部材に干渉するおそれがなく、動力伝達を確実に行うことができるようになる。しかも、ボルトのための占有スペースが不要となるので、トランスアクスルハウジング内の比較的狭い空間を効率よく使用することが可能となる。   Further, according to the differential device of the invention of claim 7, since the friction welding member of the invention of claims 1 to 6 is used, the effects of the inventions of claims 1 to 6 can be obtained. Further, when the differential ring gear and the differential case are friction-welded, the generated burrs are sealed in the voids, so that it is possible to prevent the burrs from protruding to the outside at the joint portion between the differential ring gear and the differential case. Therefore, there is no possibility of interfering with other components in the transaxle housing of the differential device, and power transmission can be performed reliably. In addition, since an occupied space for the bolt is not required, a relatively narrow space in the transaxle housing can be used efficiently.

しかも、摩擦圧接によるデフリングギヤとデフケースとの接合強度（耐疲労強度および耐衝撃強度）を高めることができるので、デフリングギヤとデフケースとの接合部に繰り返しかかる荷重を確実に対応することができる。これによっても、差動装置は動力伝達を確実に行うことができるようになる。   In addition, since the joint strength (fatigue resistance and impact strength) between the differential ring gear and the differential case by friction welding can be increased, it is possible to reliably cope with the load repeatedly applied to the joint portion between the differential ring gear and the differential case. This also enables the differential gear to reliably transmit power.

以下、図面を用いて、本発明を実施するための最良の形態について説明する。
図１は、本発明にかかる摩擦圧接部材の実施の形態の一例が適用された差動装置における、図７のＩ部に対応するデフリングギヤとデフケースとの接合部を模式的に示し、（ａ）はデフリングギヤとデフケースとの摩擦圧接前の状態を示す図、（ｂ）はデフリングギヤとデフケースとの摩擦圧接後の状態を示す図である。なお、以下の実施の形態の各例の説明において、その例より前の例の構成要素および前述の図７に示す従来例の構成要素と同じ構成要素には同じ符号を付すことにより、その詳細な説明は省略する。 Hereinafter, the best mode for carrying out the present invention will be described with reference to the drawings.
FIG. 1 schematically shows a joint between a differential ring gear and a differential case corresponding to part I in FIG. 7 in a differential device to which an example of an embodiment of a friction welding member according to the present invention is applied. ) Is a diagram showing a state before friction welding between the differential ring gear and the differential case, and (b) is a diagram showing a state after friction welding between the differential ring gear and the differential case. In the description of each example of the following embodiment, the same reference numerals are given to the same components as those of the example prior to that example and the components of the conventional example shown in FIG. The detailed explanation is omitted.

図１（ａ）に示すように、この例の摩擦圧接部材は、第１部材としての差動装置１における鋼製のデフリングギヤ２と、第２部材としての差動装置１における鋳鉄製のデフケース３とからなっている。デフリングギヤ２は、外周に形成された外歯２ａ1が形成された環状の歯部２ａを有しているとともに、この歯部２ａから連続して径方向に延設される環状の径方向部２ｂを有している。この環状の径方向部２ｂのデフケース３との接合部２ｃには、摩擦圧接される環状の凸部２ｄが形成されている。この環状の凸部２ｄのデフケース３側端から所定厚み部分は、摩擦圧接における寄り代２ｄ1として形成されている。 As shown in FIG. 1A, the friction welding member of this example includes a steel diff ring gear 2 in a differential device 1 as a first member and a cast iron diff case in the differential device 1 as a second member. It consists of three. The differential ring gear 2 has an annular tooth portion 2a formed with external teeth 2a 1 formed on the outer periphery, and an annular radial portion extending continuously from the tooth portion 2a in the radial direction. 2b. An annular convex portion 2d that is friction-welded is formed at a joint portion 2c of the annular radial portion 2b with the differential case 3. Predetermined thickness portion from the differential case 3 side end of the annular protrusion 2d is formed as a approach margin 2d 1 in friction welding.

デフリングギヤ２の接合部２ｃにおいて、環状の歯部２ａの内周端面２ａ2と環状の凸部２ｄの外周面２ｄ2との間に環状の凹部２ｅが形成されている。また、環状の凸部２ｄの内周面２ｄ3が環状の径方向部２ｂの内周端面２ｂ1より外周側に位置するように設定されている。更に、環状の凸部２ｄの内周角部が所定大きさの面取り部２ｂ2とされている。これにより、環状の凸部２ｄの内周面２ｄ3と、面取り部２ｂ2と、環状の径方向部２ｂの内周端面２ｂ1からデフケース３側に延びるように仮想した仮想線（不図示）と、環状の凸部２ｄのデフケース３側端面から内周方向に延びるように仮想した仮想線（不図示）とで区画形成される断面略四角形の環状の空間２ｆが形成されている。 At the junction 2c of the differential ring gear 2, the annular recess 2e is formed between an outer peripheral surface 2d 2 of the inner peripheral edge surface 2a 2 and the annular convex portion 2d of the annular tooth portion 2a. Further, the inner peripheral surface 2d 3 of the annular convex portion 2d is set to be positioned on the outer peripheral side from the inner peripheral end surface 2b 1 of the annular radial portion 2b. Further, the inner peripheral corner portion of the annular convex portion 2d is a chamfered portion 2b 2 having a predetermined size. Thereby, an imaginary line (not shown) that extends from the inner peripheral surface 2d 3 of the annular convex portion 2d, the chamfered portion 2b 2 and the inner peripheral end surface 2b 1 of the annular radial portion 2b to the differential case 3 side. And an annular space 2f having a substantially rectangular cross section defined by an imaginary line (not shown) extending in the inner circumferential direction from the end surface of the annular protrusion 2d on the differential case 3 side.

一方、デフケース３は、筒状の本体３ａから外方に延設された環状フランジ部３ｂを有している。本体３ａの外径は、この本体３ａがデフリングギヤ２の径方向部２ｂの内周端面２ｂ1に嵌合可能に径方向部２ｂの内径とほぼ同じ大きさに設定されている。また、環状フランジ部３ｂの外径は、この環状フランジ部３ｂがデフリングギヤ２の歯部２ａの内周端面２ａ2に嵌合可能に歯部２ａの内径とほぼ同じ大きさに設定されている。 On the other hand, the differential case 3 has an annular flange portion 3b extending outward from the cylindrical main body 3a. The outer diameter of the main body 3 a is set to be approximately the same as the inner diameter of the radial portion 2 b so that the main body 3 a can be fitted to the inner peripheral end surface 2 b 1 of the radial portion 2 b of the diff ring gear 2. The outer diameter of the annular flange portion 3b, the annular flange portion 3b is set to substantially the same size as the inner peripheral edge surface 2a 2 fittable inside diameter of the tooth portion 2a to the teeth 2a of the differential ring gear 2 .

環状フランジ部３ｂのデフリングギヤ２との接合部３ｃには、摩擦圧接される環状の凸部３ｄが形成されている。この環状の凸部３ｄは、その内、外径が環状の凸部２ｄの内、外径と等しくまたはほぼ等しく設定されているとともに、環状の凸部２ｄと軸方向に対向するようにして配設されている。また、この環状の凸部３ｄのデフリングギヤ２側端から所定厚み部分は、摩擦圧接における寄り代３ｄ1として形成されている。 An annular convex portion 3d that is friction-welded is formed at a joint portion 3c of the annular flange portion 3b with the differential ring gear 2. The annular convex portion 3d has an outer diameter that is set to be equal to or substantially equal to the outer diameter of the annular convex portion 2d, and is arranged so as to face the annular convex portion 2d in the axial direction. It is installed. The predetermined thickness portion from the ring gear 2 side end of the annular protrusion 3d is formed as a approach margin 3d 1 in friction welding.

更に、デフケース３の接合部３ｃにおいて、環状の凸部３ｄの外周面３ｄ2が環状フランジ部３ｂの外周端面３ｂ1より内周側に位置するように設定されている。これにより、環状の凸部３ｄの外周面３ｄ2と、環状フランジ部３ｂの外周端面３ｂ1からデフリングギヤ２側に延びるように仮想した仮想線（不図示）と、環状の凸部３ｄのデフリングギヤ２側端面から外周方向に延びるように仮想した仮想線（不図示）と、環状の凸部３ｄの外周面３ｄ2より外周側の環状フランジ部３ｂのデフリングギヤ２側端面３ｂ2とで区画形成される矩形断面の環状の空間３ｅが形成されている。また、本体３ａの外周面と環状の凸部３ｄの内周面３ｄ3との間には、環状の凹部３ｆが形成されている。 Further, in the joint portion 3c of the differential case 3, the outer peripheral surface 3d 2 of the annular convex portion 3d is set to be located on the inner peripheral side from the outer peripheral end surface 3b 1 of the annular flange portion 3b. Accordingly, the outer peripheral surface 3d 2 of the annular convex portion 3d, the virtual line (not shown) extending so as to extend from the outer peripheral end surface 3b 1 of the annular flange portion 3b to the differential ring gear 2 side, and the differential of the annular convex portion 3d An imaginary line (not shown) that extends from the end surface on the ring gear 2 side in the outer peripheral direction and a differential ring gear 2 side end surface 3b 2 of the annular flange portion 3b on the outer peripheral side of the outer peripheral surface 3d 2 of the annular convex portion 3d are partitioned. An annular space 3e having a rectangular cross section is formed. Between the inner circumferential surface 3d 3 of the outer circumferential surface and an annular convex portion 3d of the main body 3a, an annular recess 3f are formed.

このように構成されたデフリングギヤ２とデフケース３とが、図１（ａ）に示すように両環状の凸部２ｄ,３ｄが軸方向に対向させた状態で突き合わせられる（当接される）と、本体３ａが環状の径方向部２ｂの内周面に嵌合し、また、環状フランジ部３ｂが環状の歯部２ａの内周面に嵌合するかあるいは嵌合寸前となる。これにより、図１（ｂ）に示すように、両環状の凸部２ｄ,３ｄの外周側に、環状の凹部２ｅと環状の空間３ｅとによりほぼ密閉された環状の空所１０が形成されるとともに、両環状の凸部２ｄ,３ｄの内周側に、環状の空間２ｆと環状の凹部３ｆとによりほぼ密閉された環状の空所１１が形成されるようになっている。   When the differential ring gear 2 and the differential case 3 configured in this manner are abutted (abutted) in a state where both annular convex portions 2d and 3d face each other in the axial direction as shown in FIG. The main body 3a is fitted to the inner peripheral surface of the annular radial portion 2b, and the annular flange portion 3b is fitted to the inner peripheral surface of the annular tooth portion 2a or just before the fitting. Thereby, as shown in FIG.1 (b), the annular space 10 sealed substantially by the cyclic | annular recessed part 2e and the cyclic | annular space 3e is formed in the outer peripheral side of both cyclic | annular convex parts 2d and 3d. At the same time, an annular space 11 that is substantially sealed by an annular space 2f and an annular recess 3f is formed on the inner peripheral side of both annular projections 2d, 3d.

両環状の空所１０,１１の容積は、両寄り代２ｄ1,３ｄ1および両環状の凸部２ｄ,３ｄの各外周面２ｄ2,３ｄ2および各内周面２ｄ3,３ｄ3の大きさ、つまり両寄り代２ｄ1,３ｄ1に相当する両環状の凸部２ｄ,３ｄの体積に基づいて計算されたバリ１２の量に応じた大きさに設定されている。なお、バリ１２は、後述するように摩擦圧接におけるアプセット圧力により発生するものである。 The volume of the annular spaces 10 and 11 is larger than the margins 2d 1 and 3d 1 and the outer peripheral surfaces 2d 2 and 3d 2 and the inner peripheral surfaces 2d 3 and 3d 3 of the annular protrusions 2d and 3d. That is, the size is set in accordance with the amount of the burr 12 calculated based on the volumes of the two annular projections 2d and 3d corresponding to the offset margins 2d 1 and 3d 1 . The burr 12 is generated by the upset pressure in the friction welding as will be described later.

その場合、２つの空所１０,１１の横断面積が同じであると、外周側（摩擦圧接時に回転されるデフリングギヤ２の回転中心より遠い側）の空所１０の容積が内周側（摩擦圧接時に回転されるデフリングギヤ２の回転中心側）の空所１１の容積より大きくなるが、両寄り代２ｄ1,３ｄ1の外周側部分の量が内周側部分の量より多く、しかも摩擦圧接時での外周側部分の周速が内周側部分の周速より大きいことから外周側部分の発熱量も内周側部分の発熱量よりも多く、更にデフリングギヤ２の回転による遠心力でバリ１２が外周側に寄りがちとなるので、外周側の空所１０の横断面積を内周側の空所１１の横断面積より大きくして、外周側の空所１０の容積を内周側の空所１１の容積より更に大きく設定する。これにより、バリ１２を２つの空所１０,１１内に効率よく収容させることができる。 In that case, if the cross-sectional areas of the two cavities 10 and 11 are the same, the volume of the vacant space 10 on the outer peripheral side (the side farther from the rotation center of the diff ring gear 2 rotated during friction welding) is the inner peripheral side (friction). The volume of the space 11 on the side of the rotation center of the differential ring gear 2 that is rotated at the time of pressure contact is larger than that of the space 11, but the amount of the outer peripheral portion of both offset margins 2d 1 and 3d 1 is larger than the amount of the inner peripheral portion. Since the peripheral speed of the outer peripheral portion at the time of pressure contact is larger than the peripheral speed of the inner peripheral portion, the heat generation amount of the outer peripheral portion is larger than the heat generation amount of the inner peripheral portion, and further, the centrifugal force due to the rotation of the diff ring gear 2 Since the burrs 12 tend to move toward the outer peripheral side, the cross-sectional area of the outer peripheral space 10 is made larger than the cross-sectional area of the inner peripheral space 11 so that the volume of the outer peripheral space 10 is increased to the inner peripheral side. It is set larger than the volume of the void 11. Thereby, the burr | flash 12 can be efficiently accommodated in the two empty spaces 10 and 11.

次に、これらのデフリングギヤ２とデフケース３とを摩擦圧接により接合する方法について説明する。
デフリングギヤ２の環状の凸部２ｄとデフケース３の環状の凸部３ｄとを軸方向に一定圧力で加圧接触させた状態で、デフケース３を固定し、デフリングギヤ２を前述の一定圧力の下で所定の回転数で回転させる。すると、両環状の凸部２ｄ,３ｄの圧接部にこの回転による摩擦熱が発生し、この摩擦熱により両環状の凸部２ｄ,３ｄの圧接部が加熱される。両環状の凸部２ｄ,３ｄの圧接部が適度に加熱されて適度に柔軟になったところで、デフリングギヤ２の回転を停止して環状の凸部２ｄと環状の凸部３ｄとの加圧力を増大（アプセット）する。これにより、加熱部表面の酸化物の異物等が当接部の外に追い出されて、デフリングギヤ２およびデフケース３の両加熱当接部に新生面が現れる。そして、摩擦圧接における寄り代２ｄ1,３ｄ1分だけ、環状の凸部２ｄと環状の凸部３ｄとが互いに押し付けられると、これらの新生面どうしが互いに接合されて、高温状態で拡散された高強度の金属接合が得られる。その場合、環状の凸部２ｄと環状の凸部３ｄとの接合面の外周端には、応力が集中する箇所は生じない。 Next, a method of joining the differential ring gear 2 and the differential case 3 by friction welding will be described.
In a state where the annular convex portion 2d of the differential ring gear 2 and the annular convex portion 3d of the differential case 3 are in pressure contact with each other at a constant pressure in the axial direction, the differential case 3 is fixed, and the differential ring gear 2 is subjected to the aforementioned constant pressure. To rotate at a predetermined rotational speed. Then, frictional heat due to this rotation is generated at the pressure contact portions of both annular projections 2d and 3d, and the pressure contact portions of both annular projections 2d and 3d are heated by this frictional heat. When the pressure contact portions of both annular projections 2d and 3d are moderately heated and moderately flexible, the rotation of the diff ring gear 2 is stopped and the pressure between the annular projection 2d and the annular projection 3d is increased. Increase (upset). As a result, oxide foreign matter or the like on the surface of the heating portion is driven out of the contact portion, and new surfaces appear on both the heat contact portions of the diff ring gear 2 and the differential case 3. When the annular convex portion 2d and the annular convex portion 3d are pressed against each other by the margins 2d 1 and 3d 1 in the friction welding, these new surfaces are joined to each other and diffused in a high temperature state. A strong metal bond is obtained. In that case, the location where stress concentrates does not arise in the outer peripheral end of the joint surface of the annular convex part 2d and the annular convex part 3d.

図１（ｂ）に示すように、当接部の外に追い出された異物等によりバリ１２（多数の点で図示）が生じ、このバリ１２は空所１０,１１内に収容される。その場合、図２（ａ）ないし（ｃ）に示すように、バリ１２は、デフリングギヤ２およびデフケース３の各凸部２ｄ,３ｄの加熱部の各内外周面２ｄ3,２ｄ2;３ｄ3,３ｄ2からそれぞれ径方向に延び出すようにして発生する。空所１０,１１内に収容されたバリ１２はこれらの空所１０,１１の外に漏出することはなく、空所１０,１１内に封じ込められる。 As shown in FIG. 1 (b), a burr 12 (shown in many points) is generated by foreign matter or the like expelled from the contact portion, and this burr 12 is accommodated in the voids 10 and 11. In this case, as shown in FIGS. 2 (a) to 2 (c), the burr 12 is formed on the inner and outer peripheral surfaces 2d 3 , 2d 2 ; 3d 3 of the heating portions of the convex portions 2d and 3d of the differential ring gear 2 and the differential case 3. , 3d 2 to extend in the radial direction. The burr 12 accommodated in the cavities 10 and 11 does not leak out of these cavities 10 and 11 but is contained in the cavities 10 and 11.

なお、摩擦圧接時にデフケース３を固定する理由は、デフリングギヤ２の回転を停止して、アプセットを開始する時点で加熱部の冷却が開始されるが、このとき、デフケース３を構成する鋳鉄に冷却速度が速いと脆い組織ができてしまうので、デフケース３の方を固定することが好ましいためである。   The reason for fixing the differential case 3 at the time of friction welding is that when the rotation of the differential ring gear 2 is stopped and the upset is started, the cooling of the heating part is started. At this time, the cast iron constituting the differential case 3 is cooled. This is because it is preferable to fix the differential case 3 because a brittle structure is formed when the speed is high.

ところで、差動装置１においてはデフリングギヤ２が自動変速機等の出力歯車から荷重が繰り返し受けることから、デフリングギヤ２とデフケース３との間には前述のように高い接合強度（耐疲労強度、耐衝撃強度）が求められる。しかし、デフリングギヤ２とデフケース３の両部材を摩擦圧接で接合する場合、アプセット圧力が大きくなるにしたがって、図２（ａ）ないし（ｃ）に示すように両部材の塑性流動が大きくなり、前述のバリ１２の量が多くなるばかりでなくバリ１２の形状が大きくかつ応力集中を生じやすい形状となるため、接合強度が低下する。これは、鋳鉄に含まれる球状黒鉛が片状黒鉛に変形して脆くなり、接合面近傍の鋳鉄部材の強度低下を生じるためである。   By the way, in the differential 1, since the differential ring 2 receives a load repeatedly from an output gear such as an automatic transmission, a high bonding strength (fatigue resistance, Impact strength) is required. However, when the members of the differential ring gear 2 and the differential case 3 are joined by friction welding, as the upset pressure increases, the plastic flow of both members increases as shown in FIGS. 2 (a) to (c). In addition to an increase in the amount of the burr 12, the shape of the burr 12 is large and a shape in which stress concentration is likely to occur, so that the bonding strength is reduced. This is because the spherical graphite contained in the cast iron is deformed into flaky graphite and becomes brittle, resulting in a decrease in strength of the cast iron member in the vicinity of the joint surface.

そこで、デフリングギヤ２とデフケース３との摩擦圧接を行う際には、摩擦熱を発生させるときの摩擦圧力および接合時のアプセット圧力を適宜調整することにより、バリ１２の発生量を少なくかつバリ１２の形状を小さくなるように制御して、デフリングギヤ２とデフケース３との接合強度を高めている。
この例の差動装置１の他の構成は、前述の図７に示す特許文献１に開示の差動装置１と同じである。また、この例の差動装置１の差動も特許文献１に開示の差動装置１と同じである。 Therefore, when performing friction welding between the differential ring gear 2 and the differential case 3, the friction pressure when generating the frictional heat and the upset pressure during joining are appropriately adjusted to reduce the amount of generation of the burr 12 and the burr 12 The joint strength between the differential ring gear 2 and the differential case 3 is increased by controlling the shape of the differential ring gear 2 to be small.
The other configuration of the differential device 1 of this example is the same as that of the differential device 1 disclosed in Patent Document 1 shown in FIG. Further, the differential of the differential device 1 of this example is the same as the differential device 1 disclosed in Patent Document 1.

この例の差動装置１によれば、デフリングギヤ２とデフケース３とを摩擦圧接しているので、従来のようなボルトが不要にできる。これにより、部品点数を削減することができるので、コストを低減できるとともに重量を軽減することができる。しかも、従来の差動装置１におけるボルト締めの手作業および機械作業、切削加工等によるバリ取り作業がなくなるので、接合作業の工数を効果的に削減することができ、より一層コストを低減できる。   According to the differential device 1 of this example, since the differential ring gear 2 and the differential case 3 are friction-welded, a conventional bolt can be eliminated. Thereby, since the number of parts can be reduced, the cost can be reduced and the weight can be reduced. In addition, since there is no deburring work such as manual tightening and mechanical work, cutting, or the like in the conventional differential device 1, the number of steps for the joining work can be effectively reduced, and the cost can be further reduced.

また、デフリングギヤ２とデフケース３とを摩擦圧接した際に生じる酸化物等を含むバリ１２を両空所１０,１１内に収容して封じ込めているので、バリ１２が両空所１０,１１内から漏出するのを効果的に防止できる。これにより、バリ１２がデフリングギヤ２およびデフケース３から外方に突出しないとともに、千切れてデフリングギヤ２およびデフケース３の周囲に散らばることはない。   Further, since the burrs 12 containing oxides and the like generated when the differential ring gear 2 and the differential case 3 are friction-welded are accommodated in both the cavities 10 and 11, the burrs 12 are contained in the both cavities 10 and 11. Can effectively prevent leakage. As a result, the burr 12 does not protrude outward from the differential ring gear 2 and the differential case 3, and is not cut off and scattered around the differential ring gear 2 and the differential case 3.

したがって、デフリングギヤ２とデフケース３との接合部において、バリ１２が差動装置１のトランスアクスルハウジング４内の他の構成部材に干渉するおそれがなく、動力伝達を確実に行うことができるようになる。しかも、ボルトのための占有スペースが不要となるので、トランスアクスルハウジング４内の比較的狭い空間を効率よく使用することが可能となる。   Therefore, the burr 12 does not interfere with other components in the transaxle housing 4 of the differential device 1 at the joint between the differential ring gear 2 and the differential case 3 so that power transmission can be reliably performed. Become. In addition, since an occupied space for the bolt is not required, a relatively narrow space in the transaxle housing 4 can be efficiently used.

更に、デフリングギヤ２とデフケース３との摩擦圧接を行う際、摩擦圧力およびアプセット圧力を適宜調整することにより、バリ１２の発生量を低減することができるとともに、バリ１２の形状を応力集中部を生じ難い比較的小さな形状にすることができる。これにより、摩擦圧接によるデフリングギヤ２とデフケース３との接合強度（耐疲労強度および耐衝撃強度）を高めることができ、前述のようにデフリングギヤ２とデフケース３との接合部に繰り返しかかる荷重を確実に対応することができる。したがって、差動装置１は動力伝達を確実に行うことができるようになる。   Further, when friction welding between the differential ring gear 2 and the differential case 3 is performed, the generation amount of the burr 12 can be reduced by appropriately adjusting the friction pressure and the upset pressure, and the shape of the burr 12 can be reduced by the stress concentration portion. It can be made into a relatively small shape that is unlikely to occur. Thereby, the joint strength (fatigue resistance and impact strength) of the differential ring gear 2 and the differential case 3 by friction welding can be increased, and the load repeatedly applied to the joint portion of the differential ring gear 2 and the differential case 3 as described above. It can respond reliably. Therefore, the differential device 1 can perform power transmission reliably.

更に、摩擦圧接される環状の凸部２ｄ,３ｄはそれほど高精度に形成する必要がないので、これらの凸部２ｄ,３ｄは鍛造加工あるいは鋳造加工を行った鍛造肌あるいは鋳造肌のままでよく、仕上げ加工を行う必要はない。したがって、その分、デフリングギヤ２およびデフケース３を容易に製造できるとともに、高精度が必要でない分、製造コストを低減することができる。もちろん、デフリングギヤ２およびデフケース３の摩擦圧接の当接部（つまり、接合部）は、鍛造肌あるいは鋳造肌のままでは圧接強度および精度に影響が出るため、仕上げ加工が必要である。
この例の差動装置１の他の作用効果は、図７に示す従来の差動装置１と同じである。 Furthermore, since the annular convex portions 2d and 3d that are friction-welded do not need to be formed with high precision, these convex portions 2d and 3d may remain as forged or cast skin that has been subjected to forging or casting. There is no need for finishing. Accordingly, the differential ring gear 2 and the differential case 3 can be easily manufactured correspondingly, and the manufacturing cost can be reduced because high accuracy is not required. Of course, the contact portion (that is, the joint portion) of the friction welding of the diff ring gear 2 and the differential case 3 has an influence on the pressure contact strength and accuracy if the forging skin or the casting skin is left as it is, and needs to be finished.
Other functions and effects of the differential device 1 of this example are the same as those of the conventional differential device 1 shown in FIG.

図３は、本発明にかかる摩擦圧接部材の実施の形態の他の例が適用された差動装置における、図７のＩ部に対応するデフリングギヤとデフケースとの接合部を模式的に示し、（ａ）はデフリングギヤとデフケースとの摩擦圧接前の状態を示す図、（ｂ）はデフリングギヤとデフケースとの摩擦圧接後の状態を示す図、（ｃ）は（ｂ）におけるIIIC−IIIC線に沿う断面図である。   FIG. 3 schematically shows a joint part between the differential ring gear and the differential case corresponding to part I in FIG. 7 in a differential device to which another example of the embodiment of the friction welding member according to the present invention is applied. (A) is a figure which shows the state before the friction welding of a differential ring gear and a differential case, (b) is a figure which shows the state after the friction welding of a differential ring gear and a differential case, (c) is the IIIC-IIIC line | wire in (b) FIG.

図３（ａ）ないし（ｃ）に示すように、この例の差動装置１では、デフリングギヤ２に直方体からなる複数のキー状の突起１３が設けられている。これらのキー状の突起１３は凹部２ｅ内に位置して、環状の歯部２ａの内周面および環状の径方向部２ｂのデフケース３側の面からそれぞれ突設されてデフリングギヤ２と単一部材で一体に設けられている。また、図３（ｃ）に示すように、これらのキー状の突起１３は周方向に等間隔に形成されている。もちろん、これらのキー状の突起１３は必ずしも周方向に等間隔に形成する必要はなく、任意に設けることができる。   As shown in FIGS. 3A to 3C, in the differential device 1 of this example, a plurality of key-like protrusions 13 made of a rectangular parallelepiped are provided on the differential ring gear 2. These key-shaped projections 13 are located in the recess 2e and project from the inner peripheral surface of the annular tooth portion 2a and the surface on the differential case 3 side of the annular radial portion 2b, respectively. The members are provided integrally. Further, as shown in FIG. 3C, these key-shaped protrusions 13 are formed at equal intervals in the circumferential direction. Of course, these key-shaped protrusions 13 do not necessarily have to be formed at equal intervals in the circumferential direction, and can be arbitrarily provided.

そして、この例の差動装置１の場合、バリ１２の量、空所１０の大きさ（容量）、キー状の突起１３の幅（図において左右方向つまり外歯２ａ1の歯幅方向の長さ）および高さ（図において上下方向つまり径方向の長さ）を、発生するバリ１２がキー状の突起１３に確実に係合するように適宜設定されている。 In the case of the differential device 1 of this embodiment, the amount of burr 12, the size of the cavity 10 (volume), the width of the key-like projections 13 (in the tooth width direction of the left-right direction, that outer teeth 2a 1 in FIG lengths And the height (length in the vertical direction or radial direction in the figure) are appropriately set so that the generated burr 12 can reliably engage with the key-like protrusion 13.

このようにキー状の突起１３を設けることで、空所１０内にバリ１２が収容されたとき、このバリ１２はこれらのキー状の突起１３に係合するようになる。これにより、環状の歯部２ａから環状の径方向部２ｂへのトルク伝達をより確実に行うことができる。
この例の差動装置１の他の構成および他の作用効果は、前述の図１に示す例と同じである。
なお、外周側の突起１３を省略して、内周側の突起１４のみを設けることもできる。 By providing the key-like projections 13 in this way, when the burrs 12 are accommodated in the voids 10, the burrs 12 come to engage with these key-like projections 13. Thereby, torque transmission from the annular tooth portion 2a to the annular radial portion 2b can be performed more reliably.
Other configurations and other operational effects of the differential device 1 of this example are the same as those of the example shown in FIG.
Note that the outer peripheral projection 13 may be omitted and only the inner peripheral projection 14 may be provided.

図４は、本発明にかかる摩擦圧接部材の実施の形態の更に他の例が適用された差動装置における、図７のＩ部に対応するデフリングギヤとデフケースとの接合部を模式的に示し、（ａ）は図３（ｂ）と同様のデフリングギヤとデフケースとの摩擦圧接後の状態を示す図、（ｂ）は（ａ）におけるIVB−IVB線に沿う断面図である。
前述の図３（ａ）ないし（ｃ）に示す例では、キー状の突起１３が外周側の空所１０内に位置するように設けられているが、図４（ａ）および（ｂ）に示すように、この例の差動装置１では、外周側のキー状の突起１３に加えて、直方体の所定数のキー状の突起１４が内周側の空所１１内にも位置するように設けられている。 FIG. 4 schematically shows a joint portion between the differential ring gear and the differential case corresponding to the portion I in FIG. 7 in a differential device to which still another example of the embodiment of the friction welding member according to the present invention is applied. (A) is a figure which shows the state after the friction welding of the diff ring gear and differential case similar to FIG.3 (b), (b) is sectional drawing which follows the IVB-IVB line | wire in (a).
In the example shown in FIGS. 3 (a) to 3 (c), the key-like protrusion 13 is provided so as to be positioned in the void 10 on the outer peripheral side, but in FIGS. 4 (a) and 4 (b). As shown, in the differential device 1 of this example, in addition to the key-shaped protrusions 13 on the outer peripheral side, a predetermined number of key-shaped protrusions 14 in a rectangular parallelepiped are also located in the void 11 on the inner peripheral side. Is provided.

これらのキー状の突起１４は凹部３ｆ内に位置して、本体３ａの外周面および環状フランジ部３ｂのデフリングギヤ２側の面からそれぞれ突設されてデフケース３と単一部材で一体に設けられている。各突起１４は外周側の各突起１３に比べて小さく形成されている。また、図４の左側の図に示すように、これらのキー状の突起１４は周方向に等間隔に形成されている。その場合、キー状の突起１４は隣接する外周側のキー状の突起１３間の周方向中央位置に配置されている。もちろん、これらのキー状の突起１４は必ずしも周方向に等間隔に形成する必要はないとともに、外周側のキー状の突起１３間の周方向中央位置に配置される必要もなく、任意に設けることができる。   These key-like protrusions 14 are located in the recess 3f, and are respectively provided so as to protrude from the outer peripheral surface of the main body 3a and the surface of the annular flange portion 3b on the side of the differential ring gear 2, and are provided integrally with the differential case 3 as a single member. ing. Each protrusion 14 is formed smaller than each protrusion 13 on the outer peripheral side. Further, as shown in the diagram on the left side of FIG. 4, these key-shaped protrusions 14 are formed at equal intervals in the circumferential direction. In that case, the key-shaped protrusion 14 is disposed at the center position in the circumferential direction between the adjacent key-shaped protrusions 13 on the outer peripheral side. Of course, these key-like protrusions 14 do not necessarily have to be formed at equal intervals in the circumferential direction, and need not be arranged at the center position in the circumferential direction between the key-like protrusions 13 on the outer peripheral side, and may be provided arbitrarily. Can do.

そして、この例の空所１１に収容されるバリ１２の場合も、バリ１２の量、空所１１の大きさ（容量）、キー状の突起１４の幅（図において左右方向つまり外歯２ａ1の歯幅方向の長さ）および高さ（図において上下方向つまり径方向の長さ）を、発生するバリ１２がキー状の突起１４に確実に係合するように適宜設定されている。 In the case of the burr 12 accommodated in the space 11 of this example, the amount of the burr 12, the size (capacity) of the space 11, and the width of the key-shaped protrusion 14 (in the left-right direction, that is, the external teeth 2a 1 in the figure). The length in the tooth width direction) and the height (in the figure, the vertical direction, that is, the length in the radial direction) are appropriately set so that the generated burr 12 reliably engages with the key-shaped protrusion 14.

このように、内周側にもキー状の突起１４を設けることで、空所１１内にバリ１２が収容されたとき、このバリ１２はこれらのキー状の突起１４に係合するようになる。これにより、バリ１２と突起１４との係合によっても、環状の歯部２ａから環状の径方向部２ｂへのトルク伝達を行うことができるので、前述の図３に示す例よりも、トルク伝達をより一層確実に行うことができるようになる。
この例の差動装置１の他の構成および他の作用効果は、前述の図３に示す例と同じである。 Thus, by providing the key-shaped protrusions 14 on the inner peripheral side, when the burrs 12 are accommodated in the voids 11, the burrs 12 are engaged with these key-shaped protrusions 14. . As a result, torque transmission from the annular tooth portion 2a to the annular radial portion 2b can be performed even by engagement between the burr 12 and the protrusion 14, so that torque transmission can be achieved as compared with the example shown in FIG. Can be performed more reliably.
Other configurations and other functions and effects of the differential device 1 of this example are the same as those of the example shown in FIG.

図５は、本発明にかかる摩擦圧接部材の実施の形態の更に他の例が適用された差動装置における、図７のＩ部に対応するデフリングギヤとデフケースとの接合部を模式的に示し、（ａ）は図３（ｂ）と同様のデフリングギヤとデフケースとの摩擦圧接後の状態を示す図、（ｂ）は（ａ）におけるVB−VB線に沿う断面図である。
前述の図３（ａ）ないし（ｂ）に示す例では、キー状の突起１３が外周側の空所１０内に配置されているが、図５（ａ）および（ｂ）に示すように、この例の差動装置１では、キー状の突起１３に代えて、スプライン１５が外周側の空所１０内に位置するようにして設けられている。このスプライン１５は、環状の歯部２ａの内周面に形成されている。 FIG. 5 schematically shows a joint portion between the differential ring gear and the differential case corresponding to the portion I in FIG. 7 in a differential device to which still another example of the embodiment of the friction welding member according to the present invention is applied. (A) is a figure which shows the state after the friction welding of the diff ring gear and differential case similar to FIG.3 (b), (b) is sectional drawing which follows the VB-VB line | wire in (a).
In the example shown in FIGS. 3 (a) to 3 (b), the key-like protrusion 13 is disposed in the outer space 10 but, as shown in FIGS. 5 (a) and 5 (b), In the differential device 1 of this example, a spline 15 is provided so as to be located in the outer space 10 in place of the key-shaped protrusion 13. The spline 15 is formed on the inner peripheral surface of the annular tooth portion 2a.

そして、この例の空所１０に収容されるバリ１２の場合も、バリ１２の量、空所１０の大きさ（容量）、スプライン１５の幅（図において左右方向つまり外歯２ａ1の歯幅方向の長さ）および高さ（図において上下方向つまり径方向の長さ）を、発生するバリ１２がスプライン１５に確実に係合するように適宜設定されている。これにより、空所１０内に収容されるバリ１２がこのスプライン１５に係合するようになる。これにより、環状の歯部２ａから環状の径方向部２ｂへのトルク伝達をより確実に行うことができる。
この例の差動装置１の他の構成および他の作用効果は、前述の図１に示す例と同じである。
なお、スプラインは外周側の空所１０に設けることに加えて、内周側の空所１１にも設けることができる。その場合には、スプラインはデフケース３の本体３ａの外周面に形成される。また、スプラインは内周側の空所１１のみに設けることができる。 Also in the case of the burr 12 accommodated in the void 10 of this example, the amount of the burr 12, the size (capacity) of the void 10, and the width of the spline 15 (the width of the teeth in the left-right direction, that is, the external teeth 2a 1 in the figure). The length in the direction) and the height (in the drawing, the vertical direction, that is, the length in the radial direction) are appropriately set so that the generated burr 12 reliably engages with the spline 15. As a result, the burr 12 accommodated in the void 10 is engaged with the spline 15. Thereby, torque transmission from the annular tooth portion 2a to the annular radial portion 2b can be performed more reliably.
Other configurations and other operational effects of the differential device 1 of this example are the same as those of the example shown in FIG.
The spline can be provided not only in the outer space 10 but also in the inner space 11. In that case, the spline is formed on the outer peripheral surface of the main body 3 a of the differential case 3. Further, the spline can be provided only in the space 11 on the inner peripheral side.

図６は、本発明におけるデフリングギヤとデフケースに設けられる空所の変形例を示す図である。その場合、（ａ）ないし（ｃ）は空所の形状の変形例を示し、（１）ないし（４）は空所の個数の変形例を示している。
そして、両凸部２ｄ,３ｄの接合面およびその近傍部分は、摩擦圧接時の発熱とその後の冷却により硬化するが、強度の低下は起きないように摩擦圧接の条件が設定される。 FIG. 6 is a view showing a modification of the space provided in the differential ring gear and the differential case in the present invention. In that case, (a) to (c) show variations of the shape of the voids, and (1) to (4) show variations of the number of voids.
The joint surfaces of both convex portions 2d and 3d and the vicinity thereof are cured by heat generation during the friction welding and subsequent cooling, but the friction welding conditions are set so that the strength does not decrease.

図６（ａ）,（１）に示す例では、断面矩形に形成された外周側の空所１０と、同じく断面矩形に形成された内周側の空所１１とが形成されている。つまり、矩形の空所が２箇所に設けられている。また、図６（ａ）,（２）に示す例では、断面矩形に形成された外周側の空所１０と、同じく断面矩形に形成された内周側の空所１１と、これらの空所１０,１１の間に、更に１つの矩形の空所１６が形成されている。つまり、矩形の空所が３箇所に設けられている。更に、図６（ａ）,（３）に示す例では、断面矩形に形成された外周側の空所１０と、同じく矩形に形成された内周側の空所１１と、これらの空所１０,１１の間に、更に２つの断面矩形の空所１６,１７が形成されている。つまり、矩形の空所が４箇所に設けられている。更に、図６（ａ）,（４）に示す例では、断面矩形に形成された外周側の空所１０と、同じく断面矩形に形成された内周側の空所１１と、これらの空所１０,１１の間に、更に断面矩形に形成された４つの空所１６,１７,１８,１９が形成されている。つまり、矩形の空所が６箇所に設けられている。   In the example shown in FIGS. 6A and 6A, an outer peripheral space 10 having a rectangular cross section and an inner peripheral space 11 having a rectangular cross section are formed. That is, two rectangular voids are provided. In the example shown in FIGS. 6A and 6B, the outer peripheral space 10 formed in a rectangular cross section, the inner peripheral space 11 also formed in a rectangular cross section, and these empty spaces. A further rectangular space 16 is formed between 10 and 11. That is, rectangular voids are provided at three locations. Furthermore, in the example shown in FIGS. 6A and 6C, the outer peripheral space 10 formed in a rectangular cross section, the inner peripheral space 11 formed in the same rectangular shape, and these empty spaces 10. , 11 are further formed with two voids 16, 17 having a rectangular cross section. That is, rectangular voids are provided at four locations. Furthermore, in the example shown in FIGS. 6A and 6B, the outer peripheral space 10 formed in a rectangular cross section, the inner peripheral space 11 also formed in a rectangular cross section, and these empty spaces. Further, four cavities 16, 17, 18, and 19 having a rectangular cross section are formed between 10 and 11. That is, six rectangular spaces are provided.

更に、図６（ｂ）,（１）に示す例では、断面菱形に形成された外周側の空所１０と、同じく断面菱形に形成された内周側の空所１１とが形成されている。つまり、菱形の空所が２箇所に設けられている。また、図６（ｂ）,（２）に示す例では、断面菱形に形成された外周側の空所１０と、同じく断面菱形に形成された内周側の空所１１と、これらの空所１０,１１の間に、更に１つの断面菱形の空所１６が形成されている。つまり、菱形の空所が３箇所に設けられている。更に、図６（ｂ）,（３）に示す例では、断面菱形に形成された外周側の空所１０と、同じく断面菱形に形成された内周側の空所１１と、これらの空所１０,１１の間に、更に２つの断面菱形の空所１６,１７が形成されている。つまり、菱形の空所が４箇所に設けられている。更に、図６（ｂ）,（４）に示す例では、断面菱形に形成された外周側の空所１０と、同じく断面菱形に形成された内周側の空所１１と、これらの空所１０,１１の間に、更に４つの断面菱形の空所１６,１７,１８,１９が形成されている。つまり、菱形の空所が６箇所に設けられている。   Furthermore, in the example shown in FIGS. 6B and 6A, an outer peripheral space 10 formed in a diamond shape and an inner peripheral space 11 formed in a diamond shape are formed. . That is, rhombus voids are provided in two places. In the example shown in FIGS. 6B and 6B, the outer peripheral space 10 formed in a diamond shape, the inner peripheral space 11 formed in a diamond shape, and these voids. A space 16 having a diamond-shaped cross section is formed between 10 and 11. That is, rhombus voids are provided at three locations. Further, in the example shown in FIGS. 6B and 6C, the outer peripheral space 10 formed in a rhombus cross section, the inner peripheral space 11 formed in the same cross section rhombus, and these voids. Further, two voids 16 and 17 having a diamond-shaped cross section are formed between 10 and 11. That is, four diamond-shaped voids are provided. Further, in the example shown in FIGS. 6B and 6B, the outer peripheral space 10 formed in a diamond shape in the cross section, the inner peripheral space 11 formed in a diamond shape in the same manner, and these empty spaces. Further, four voids 16, 17, 18, and 19 having a diamond-shaped cross section are formed between 10 and 11. That is, there are six diamond-shaped voids.

更に、図６（ｃ）,（１）に示す例では、断面円形に形成された外周側の空所１０と、同じく断面円形に形成された内周側の空所１１とが形成されている。つまり、円形の空所が２箇所に設けられている。また、図６（ｃ）,（２）に示す例では、断面円形に形成された外周側の空所１０と、同じく断面円形に形成された内周側の空所１１と、これらの空所１０,１１の間に、更に１つの断面円形の空所１６が形成されている。つまり、円形の空所が３箇所に設けられている。更に、図６（ｃ）,（３）に示す例では、断面円形状に形成された外周側の空所１０と、同じく断面円形に形成された内周側の空所１１と、これらの空所１０,１１の間に、更に２つの断面円形の空所１６,１７が形成されている。つまり、円形の空所が４箇所に設けられている。更に、図６（ｃ）,（４）に示す例では、断面円形に形成された外周側の空所１０と、同じく断面円形に形成された内周側の空所１１と、これらの空所１０,１１の間に、更に４つの断面円形の空所１６,１７,１８,１９が形成されている。つまり、円形の空所が６箇所に設けられている。
そして、図６において（１）から（４）に向かって空所の個数が順次多くなるに従って、バリ１２の排出し易さが大きくなる。 Further, in the example shown in FIGS. 6C and 6A, an outer peripheral space 10 formed in a circular cross section and an inner peripheral space 11 formed in a circular cross section are formed. . In other words, two circular voids are provided. In the example shown in FIGS. 6C and 6B, the outer peripheral space 10 formed in a circular cross section, the inner peripheral space 11 formed in a circular cross section, and these empty spaces. A space 16 having a circular cross section is further formed between 10 and 11. That is, three circular cavities are provided. Further, in the example shown in FIGS. 6C and 6C, the outer peripheral space 10 formed in a circular cross section, the inner peripheral space 11 also formed in a circular cross section, and these empty spaces. Between the locations 10 and 11, two additional spaces 16 and 17 having a circular cross section are formed. That is, four circular voids are provided. Further, in the example shown in FIGS. 6C and 6D, the outer peripheral space 10 formed in a circular cross section, the inner peripheral space 11 formed in a circular cross section, and these empty spaces. Further, four cavities 16, 17, 18, 19 having a circular section are formed between 10, 11. That is, there are six circular voids.
In FIG. 6, as the number of voids increases sequentially from (1) to (4), the ease of discharging the burr 12 increases.

なお、図６に示す例では、空所１０,１１,１６,１７,１８,１９がいずれも閉空間として形成されているが、本発明の摩擦圧接部材はこれに限定されるものではなく、外周側の空所１０と内周側の空所１１は開空間として形成することもできる。その場合には、バリ１２はこれらの開空間の空所１０,１１内に収容されるようにすればよい。しかし、本発明の摩擦圧接部材を前述の各例のような差動装置１等の２部材間でトルク伝達を行う機械装置に適用する場合等には、バリ１２が千切れて周囲の他の部材に支障を来すおそれが考えられるので、外周側の空所１０と内周側の空所１１を閉空間に形成して、バリ１２をこれらの空間１０,１１内に封じ込めることが好ましい。   In the example shown in FIG. 6, the voids 10, 11, 16, 17, 18, and 19 are all formed as closed spaces, but the friction welding member of the present invention is not limited to this, The outer space 10 and the inner space 11 can be formed as open spaces. In that case, the burr 12 may be accommodated in the voids 10 and 11 of these open spaces. However, when the friction welding member of the present invention is applied to a mechanical device that transmits torque between two members such as the differential device 1 as in the above-described examples, the burr 12 is broken and other surroundings are used. Since there is a possibility that the member may be hindered, it is preferable that the outer space 10 and the inner space 11 are formed in a closed space and the burr 12 is enclosed in these spaces 10 and 11.

また、前述の各例では、鋼からなるデフリングギヤ２と鋳鉄からなるデフケース３とを摩擦圧接で接合するものとしているが、本発明の摩擦圧接部材はこれに限定されるものではなく、接合部にバリ１２が封じ込められる空所が形成可能であれば、例えば、中空の丸棒や中実の丸棒等の他の２つの部材の摩擦圧接にも適用できる。更に、本発明が適用可能な摩擦圧接される２つの材料としては、鋼と鋼のような同種金属材料、あるいは前述の例のような鋼と鋳鉄や鋼とアルミ等の異種金属材料がある。その場合、摩擦圧接を行うにあたっては、アプセットを開始する時点で加熱部が冷却開始されるため、２つの部材のうち、冷却速度が速いと脆い組織ができる部材の方を固定し、冷却速度が速くても組織がほとんど変わらない部材の方を回転させるのが好ましい。   In each of the above examples, the differential ring gear 2 made of steel and the differential case 3 made of cast iron are joined by friction welding, but the friction welding member of the present invention is not limited to this, If it is possible to form a space in which the burr 12 can be contained, it can be applied to friction welding of two other members such as a hollow round bar and a solid round bar. Further, the two materials to be friction welded to which the present invention can be applied include the same metal materials such as steel and steel, or different metal materials such as steel and cast iron, steel and aluminum as in the above-described examples. In that case, when performing friction welding, since the heating part starts cooling when the upset is started, the member that forms a brittle structure when the cooling rate is fast is fixed, and the cooling rate is fixed. It is preferable to rotate the member whose structure hardly changes even if it is fast.

更に、前述の例では、デフリングギヤ２が環状に形成されるとともにデフケース３が筒状に形成されることから、各寄り代２ｄ1,３ｄ1が形成される凸部２ｄ,３ｄがともに環状（円筒状）に形成されているが、２つの中実部材の接合では、凸部２ｄ,３ｄはともに環状（円筒状）に形成する必要はなく、円柱状に形成することもできる。もちろん、２つの中実部材の接合でも、凸部２ｄ,３ｄを環状（円筒状）に形成することができることは言うまでもない。 Furthermore, in the above-described example, since the differential ring gear 2 is formed in an annular shape and the differential case 3 is formed in a cylindrical shape, the convex portions 2d and 3d on which the shift margins 2d 1 and 3d 1 are formed are both annular ( In the joining of two solid members, the projections 2d and 3d do not need to be formed in an annular shape (cylindrical shape), but can be formed in a columnar shape. Of course, it is needless to say that the convex portions 2d and 3d can be formed in an annular shape (cylindrical shape) by joining two solid members.

本発明の摩擦圧接部材は、例えば自動車の差動装置等の種々の装置に用いられ、金属からなる２つの構成部材を接合して構成される接合部材、特に、繰り返し荷重を受ける部材とこの部材を支持する部材とが互いに接合されて構成される接合部材に好適に利用することが可能である。
また、本発明の差動装置は、例えば自動車の差動装置等の種々の機械装置の差動装置に好適に利用することが可能である。 The friction welding member of the present invention is used in various devices such as a differential of an automobile, for example, and is a joining member formed by joining two constituent members made of metal, particularly a member that receives a repeated load and this member. It is possible to use suitably for the joining member comprised by mutually joining with the member which supports.
Further, the differential device of the present invention can be suitably used for a differential device of various mechanical devices such as an automobile differential device.

本発明にかかる摩擦圧接部材の実施の形態の一例が適用された差動装置におけるデフリングギヤとデフケースとの接合部を模式的に示し、（ａ）はデフリングギヤとデフケースとの摩擦圧接前の状態を示す図、（ｂ）はデフリングギヤとデフケースとの摩擦圧接後の状態を示す図である。The junction part of a differential ring gear and a differential case in the differential gear to which an example of an embodiment of the friction welding member concerning the present invention is applied is shown typically, (a) is the state before friction welding of a differential ring gear and a differential case FIG. 5B is a diagram illustrating a state after friction welding between the differential ring gear and the differential case. 摩擦圧接を説明し、（ａ）は一般的な圧接条件による摩擦圧接の説明図、（ｂ）は本発明によるソフト圧接条件による摩擦圧接の説明図である。Frictional pressure welding will be described. (A) is an explanatory diagram of friction welding under a general pressure welding condition, and (b) is an explanatory diagram of friction welding under a soft pressure welding condition according to the present invention. 本発明にかかる摩擦圧接部材の実施の形態の他の例が適用された差動装置におけるデフリングギヤとデフケースとの接合部を模式的に示し、（ａ）はデフリングギヤとデフケースとの摩擦圧接前の状態を示す図、（ｂ）はデフリングギヤとデフケースとの摩擦圧接後の状態を示す図、（ｃ）は（ｂ）におけるIIIC−IIIC線に沿う断面図である。FIG. 5 schematically shows a joint portion between a differential ring gear and a differential case in a differential gear to which another example of the embodiment of the friction welding member according to the present invention is applied, and FIG. (B) is a figure which shows the state after the friction welding of a diff ring gear and a differential case, (c) is sectional drawing which follows the IIIC-IIIC line | wire in (b). 本発明にかかる摩擦圧接部材の実施の形態の更に他の例が適用された差動装置におけるデフリングギヤとデフケースとの接合部を模式的に示し、（ａ）は図３（ｂ）と同様のデフリングギヤとデフケースとの摩擦圧接後の状態を示す図、（ｂ）は（ａ）におけるIVB−IVB線に沿う断面図である。The junction part of the differential ring gear and the differential case in the differential gear to which still another example of the embodiment of the friction welding member according to the present invention is applied is schematically shown, and (a) is the same as FIG. 3 (b). The figure which shows the state after the friction welding of a differential ring gear and a differential case, (b) is sectional drawing which follows the IVB-IVB line | wire in (a). 本発明にかかる摩擦圧接部材の実施の形態の更に他の例が適用された差動装置におけるデフリングギヤとデフケースとの接合部を模式的に示し、（ａ）は図３（ｂ）と同様のデフリングギヤとデフケースとの摩擦圧接後の状態を示す図、（ｂ）は（ａ）におけるVB−VB線に沿う断面図である。The junction part of the differential ring gear and the differential case in the differential gear to which still another example of the embodiment of the friction welding member according to the present invention is applied is schematically shown, and (a) is the same as FIG. 3 (b). The figure which shows the state after the friction welding of a differential ring gear and a differential case, (b) is sectional drawing which follows the VB-VB line | wire in (a). 本発明にかかるデフリングギヤとデフケースとの接合部に設けられる空所の変形例を示す図である。It is a figure which shows the modification of the space provided in the junction part of the differential ring gear and differential case concerning this invention. 特許文献１に開示の従来の差動装置を示す断面図である。It is sectional drawing which shows the conventional differential device disclosed by patent document 1. FIG.

符号の説明Explanation of symbols

１…差動装置、２…デフリングギヤ、２ｃ…接合部、２ｄ…凸部、２ｄ1…寄り代、２ｅ…凹部、２ｆ…空間、３…デフケース、３ｃ…接合部、３ｄ…凸部、３ｄ1…寄り代、３ｅ…空間、３ｆ…凹部、１０,１１,１６,１７,１８,１９…空所、１２…バリ 1 ... differential, 2 ... differential ring gear, 2c ... junction, 2d ... protrusion, 2d 1 ... approach margin, 2e ... recess, 2f ... space, 3 ... differential case, 3c ... junction, 3d ... protrusion, 3d 1 ... close margin, 3e ... space, 3f ... concave, 10,11,16,17,18,19 ... vacant space, 12 ... burr

Claims (7)

互いに摩擦圧接される第１部材と第２部材とからなり、
前記第１部材の接合部と前記第２部材の接合部との少なくとも一方に、前記第１部材と前記第２部材が摩擦圧接される際に形成される空所を形成する空所形成部が設けられており、
前記摩擦圧接で生じるバリが前記空所に収容されるようにして前記第１部材と前記第２部材が摩擦圧接されていることを特徴とする摩擦圧接部材。 A first member and a second member that are friction-welded to each other;
A void forming portion that forms a void formed when the first member and the second member are friction-welded to at least one of the bonding portion of the first member and the bonding portion of the second member. Provided,
The friction welding member, wherein the first member and the second member are friction welded so that burrs generated by the friction welding are accommodated in the voids. 前記第１部材と前記第２部材とが互いに摩擦圧接された状態で一体回転するようになっており、前記第１部材と前記第２部材との少なくとも一方に、前記バリが係合する係合部が前記空所内に位置するようにして設けられていることを特徴とする請求項１記載の摩擦圧接部材。 The first member and the second member are integrally rotated with each other in a state of friction welding, and the burr engages with at least one of the first member and the second member. The friction welding member according to claim 1, wherein the portion is provided so as to be located in the space. 前記空所が複数設けられていることを特徴とする請求項１記載の摩擦圧接部材。 The friction welding member according to claim 1, wherein a plurality of the voids are provided. 前記複数の空所のうち、摩擦圧接される際の部材の回転の回転中心より遠い側の空所の容積が回転中心側の空所の容積より大きく設定されていることを特徴とする請求項３記載の摩擦圧接部材。 The volume of the space far from the rotation center of rotation of the member when the friction welding is performed among the plurality of spaces is set larger than the volume of the space on the rotation center side. 3. The friction welding member according to 3. 前記第１部材と前記第２部材とが互いに摩擦圧接された状態で一体回転するようになっており、前記第１部材と前記第２部材との少なくとも一方に、前記バリが係合する係合部が前記複数の空所の少なくとも１つに位置するようにして設けられていることを特徴とする請求項３または４記載の摩擦圧接部材。 The first member and the second member are integrally rotated with each other in a state of friction welding, and the burr engages with at least one of the first member and the second member. The friction welding member according to claim 3 or 4, wherein a portion is provided so as to be located in at least one of the plurality of voids. 前記係合部はキー状の突起またはスプラインからなることを特徴とする請求項２または５記載の摩擦圧接部材。 6. The friction welding member according to claim 2, wherein the engaging portion is formed of a key-shaped protrusion or a spline. 少なくともデフリングギヤと、このデフリングギヤを支持しかつデフリングギヤと一体回転するデフケースとを備えている差動装置において、
請求項１ないし６のいずれか１の摩擦圧接部材を用い、
前記第１部材がデフリングギヤであり、前記第２部材がデフケースであることを特徴とする差動装置。 In a differential device including at least a differential ring gear and a differential case that supports the differential ring gear and rotates integrally with the differential ring gear,
Using the friction welding member according to any one of claims 1 to 6,
The differential device according to claim 1, wherein the first member is a differential ring gear, and the second member is a differential case.
JP2003312683A 2003-09-04 2003-09-04 Friction pressure welding member and differential gear equipped with member Pending JP2005081351A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2003312683A JP2005081351A (en) 2003-09-04 2003-09-04 Friction pressure welding member and differential gear equipped with member

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2003312683A JP2005081351A (en) 2003-09-04 2003-09-04 Friction pressure welding member and differential gear equipped with member

Publications (2)

Publication Number Publication Date
JP2005081351A true JP2005081351A (en) 2005-03-31
JP2005081351A5 JP2005081351A5 (en) 2006-10-19

Family

ID=34413868

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2003312683A Pending JP2005081351A (en) 2003-09-04 2003-09-04 Friction pressure welding member and differential gear equipped with member

Country Status (1)

Country Link
JP (1) JP2005081351A (en)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007170622A (en) * 2005-12-26 2007-07-05 Ｇｋｎ ドライブライン トルクテクノロジー株式会社 Joint structure of torque transmission member, joining method for torque transmission member, and power transmission device using them
WO2007085848A1 (en) * 2006-01-27 2007-08-02 Meritor Heavy Vehicle Systems Cameri Spa Differential gear assembly
JP2008155247A (en) * 2006-12-22 2008-07-10 Smc Corp Friction welding method and friction welding member joined by the method
CN102059437A (en) * 2009-11-04 2011-05-18 马自达汽车株式会社 Method of bonding metallic members, and metallic bonded body
US20120094798A1 (en) * 2010-01-22 2012-04-19 Keisuke Uchida Welded structure and welding method
US8327541B2 (en) 2006-01-27 2012-12-11 Meritor Heavy Vehicle Systems Cameri Spa Method of assembling a differential mechanism
EP2567772A2 (en) 2011-09-12 2013-03-13 Jtekt Corporation Friction bonding structure and pump device
KR101344562B1 (en) * 2010-01-22 2013-12-26 도요타지도샤가부시키가이샤 Welded structure and welding method
US8747275B2 (en) 2009-01-27 2014-06-10 Toyota Jidosha Kabushiki Kaisha Differential device
JP2014188622A (en) * 2013-03-27 2014-10-06 Kitagawa Iron Works Co Ltd Index table
CN105108327A (en) * 2015-09-18 2015-12-02 张家港市和伟五金工具厂 Hardware welding method based on friction stir equipment
CN105108326A (en) * 2015-09-18 2015-12-02 张家港市和伟五金工具厂 Friction-stir hardware welding method
WO2016037757A1 (en) * 2014-09-11 2016-03-17 Volkswagen Aktiengesellschaft Method for producing a massive metal composite component, and massive metal composite component produced using said method
CN106015509A (en) * 2015-03-30 2016-10-12 武藏精密工业株式会社 Transmission device
CN106812909A (en) * 2015-11-30 2017-06-09 福特全球技术公司 Accurate alignment, the screw conic of friction welding or hypoid ring gear and case of differential assembly
CN108027035A (en) * 2015-07-20 2018-05-11 雷诺股份公司 Being welded to connect between differential ring gear and the housing of differential ring gear
CN109195725A (en) * 2016-04-01 2019-01-11 麦加戴恩国际有限公司 The ring gear of the cladding molding of differential mechanism
US10738869B2 (en) 2015-11-30 2020-08-11 Ford Global Technologies, Llc Precisely aligned, friction welded spiral bevel or hypoid ring gear and differential case assembly
JP2021021399A (en) * 2019-07-24 2021-02-18 スズキ株式会社 Differential device for automobile
CN115464248A (en) * 2022-09-15 2022-12-13 中国航空制造技术研究院 A dual-drive differential backfill friction stir spot welding spindle

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007170622A (en) * 2005-12-26 2007-07-05 Ｇｋｎ ドライブライン トルクテクノロジー株式会社 Joint structure of torque transmission member, joining method for torque transmission member, and power transmission device using them
WO2007085848A1 (en) * 2006-01-27 2007-08-02 Meritor Heavy Vehicle Systems Cameri Spa Differential gear assembly
US8015899B2 (en) 2006-01-27 2011-09-13 Meritor Heavy Vehicle Systems Cameri Spa Differential gear assembly and method
US8327541B2 (en) 2006-01-27 2012-12-11 Meritor Heavy Vehicle Systems Cameri Spa Method of assembling a differential mechanism
JP2008155247A (en) * 2006-12-22 2008-07-10 Smc Corp Friction welding method and friction welding member joined by the method
US8747275B2 (en) 2009-01-27 2014-06-10 Toyota Jidosha Kabushiki Kaisha Differential device
EP2789877A3 (en) * 2009-01-27 2016-05-18 Toyota Jidosha Kabushiki Kaisha Differential device
CN102059437A (en) * 2009-11-04 2011-05-18 马自达汽车株式会社 Method of bonding metallic members, and metallic bonded body
JP2011098358A (en) * 2009-11-04 2011-05-19 Mazda Motor Corp Method of bonding metallic members, and metallic bonded body
KR101344562B1 (en) * 2010-01-22 2013-12-26 도요타지도샤가부시키가이샤 Welded structure and welding method
US8814742B2 (en) 2010-01-22 2014-08-26 Toyota Jidosha Kabushiki Kaisha Welded structure and welding method
US9239104B2 (en) 2010-01-22 2016-01-19 Toyota Jidosha Kabushiki Kaisha Welded structure and welding method
US20120094798A1 (en) * 2010-01-22 2012-04-19 Keisuke Uchida Welded structure and welding method
JP2013059883A (en) * 2011-09-12 2013-04-04 Jtekt Corp Friction joint structure and pump device
EP2567772A2 (en) 2011-09-12 2013-03-13 Jtekt Corporation Friction bonding structure and pump device
JP2014188622A (en) * 2013-03-27 2014-10-06 Kitagawa Iron Works Co Ltd Index table
CN106604789A (en) * 2014-09-11 2017-04-26 大众汽车有限公司 Method for producing a massive metal composite component, and massive metal composite component produced using said method
WO2016037757A1 (en) * 2014-09-11 2016-03-17 Volkswagen Aktiengesellschaft Method for producing a massive metal composite component, and massive metal composite component produced using said method
CN106015509A (en) * 2015-03-30 2016-10-12 武藏精密工业株式会社 Transmission device
CN108027035A (en) * 2015-07-20 2018-05-11 雷诺股份公司 Being welded to connect between differential ring gear and the housing of differential ring gear
CN105108327A (en) * 2015-09-18 2015-12-02 张家港市和伟五金工具厂 Hardware welding method based on friction stir equipment
CN105108326A (en) * 2015-09-18 2015-12-02 张家港市和伟五金工具厂 Friction-stir hardware welding method
CN106812909A (en) * 2015-11-30 2017-06-09 福特全球技术公司 Accurate alignment, the screw conic of friction welding or hypoid ring gear and case of differential assembly
US10738869B2 (en) 2015-11-30 2020-08-11 Ford Global Technologies, Llc Precisely aligned, friction welded spiral bevel or hypoid ring gear and differential case assembly
CN106812909B (en) * 2015-11-30 2021-11-30 福特全球技术公司 Precision aligned, friction welded helical bevel or hypoid ring gear and differential case assembly
CN109195725A (en) * 2016-04-01 2019-01-11 麦加戴恩国际有限公司 The ring gear of the cladding molding of differential mechanism
JP2021021399A (en) * 2019-07-24 2021-02-18 スズキ株式会社 Differential device for automobile
CN115464248A (en) * 2022-09-15 2022-12-13 中国航空制造技术研究院 A dual-drive differential backfill friction stir spot welding spindle
CN115464248B (en) * 2022-09-15 2023-12-29 中国航空制造技术研究院 A dual-drive differential backfill friction stir spot welding spindle

Similar Documents

Publication Publication Date Title
JP2005081351A (en) Friction pressure welding member and differential gear equipped with member
US8758873B2 (en) Cast-in-place torsion joint
JP5614054B2 (en) Beam welding member and differential device provided with the same
JP5209506B2 (en) Drive member assembly mechanism comprising a shaft coupled to a rotor of a rotating machine
JP5252129B2 (en) Fastening structure of ring gear and differential case and differential using the same
JP2008539387A (en) Wheel bearing device
KR20170032193A (en) Torsional vibration reduction device for torque converter
JP2005521000A (en) Device for coupling housing device of coupling device with rotor device of electric machine
JP5750014B2 (en) Planetary gear unit
JPH06190641A (en) Method of assembling coaxial two structural elements
US20040045389A1 (en) Rotating housing and gear assembly
EP2578904B1 (en) Fastening structure for ring-gear and differential case, and differential device using same
CN113785140B (en) Differential transmission device
JP6341216B2 (en) Vehicle power transmission device
AU705964B2 (en) Friction welded shaft
JP5124232B2 (en) Power transmission component and manufacturing method thereof
US20040055845A1 (en) Housing arrangement for a friction clutch
JP2001124180A (en) Composite gear
JP2007230341A (en) Vehicle drive device
EP4015873B1 (en) A gear wheel and a vehicle transmission arrangement
JP2006175547A (en) Electric tool and gear device
JP2001074060A (en) Sliding yoke and manufacture thereof
CN111173913A (en) Torque converter, powertrain and motor vehicle including same, and method of manufacture
JP2009174629A (en) Vehicle drive device
JP2017110741A (en) Vehicle power transmission device

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20060830

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20060904

A977 Report on retrieval

Effective date: 20081210

Free format text: JAPANESE INTERMEDIATE CODE: A971007

A131 Notification of reasons for refusal

Effective date: 20090204

Free format text: JAPANESE INTERMEDIATE CODE: A131

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20090402

A02 Decision of refusal

Effective date: 20091111

Free format text: JAPANESE INTERMEDIATE CODE: A02