JPH01283434A - Telescopic joint shaft - Google Patents
Telescopic joint shaftInfo
- Publication number
- JPH01283434A JPH01283434A JP1060579A JP6057989A JPH01283434A JP H01283434 A JPH01283434 A JP H01283434A JP 1060579 A JP1060579 A JP 1060579A JP 6057989 A JP6057989 A JP 6057989A JP H01283434 A JPH01283434 A JP H01283434A
- Authority
- JP
- Japan
- Prior art keywords
- joint
- shaft
- neck
- joint shaft
- length
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000005096 rolling process Methods 0.000 claims abstract description 9
- 230000008878 coupling Effects 0.000 claims abstract description 4
- 238000010168 coupling process Methods 0.000 claims abstract description 4
- 238000005859 coupling reaction Methods 0.000 claims abstract description 4
- 239000000314 lubricant Substances 0.000 claims description 2
- 238000007789 sealing Methods 0.000 claims 1
- 238000005452 bending Methods 0.000 abstract description 4
- 230000005540 biological transmission Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 230000004323 axial length Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 210000002445 nipple Anatomy 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
- F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
- F16D3/42—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with ring-shaped intermediate member provided with bearings or inwardly-directed trunnions
- F16D3/43—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with ring-shaped intermediate member provided with bearings or inwardly-directed trunnions with ball or roller bearings
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/202—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints
- F16D3/205—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part
- F16D3/2055—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part having three pins, i.e. true tripod joints
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
- F16D3/30—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected in which the coupling is specially adapted to constant velocity-ratio
- F16D3/32—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected in which the coupling is specially adapted to constant velocity-ratio by the provision of two intermediate members each having two relatively perpendicular trunnions or bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、２つの自在継手と、長さ可変の軸部分とを有
する、請求項第１項のプレアンブルに記載の継手軸に関
する。この種の継手軸は、西独公開第２，８０９，６６
５号（米国特許第４．２７１Ｊ６８５号）から公知であ
る。DETAILED DESCRIPTION OF THE INVENTION The invention relates to a joint shaft according to the preamble of claim 1, having two universal joints and a shaft portion of variable length. This type of joint shaft is described in West German Publication No. 2,809,66.
No. 5 (U.S. Pat. No. 4,271J685).
自動車に使用される継手軸は、一般に、例えば、トラン
スミッションと駆動軸との間の比較的大きい間隔を橋か
けしなければならない。この場合、概ね、運転時、変化
する有効荷重およびバネの遊びによる高さ差および長さ
変化も補償する必要がある。従って、大きい屈曲角およ
び長さ補償性が得られるよう継手を設計しなければなら
ない。かくして、継手および軸の軸線方向構造長さが大
きくなる。この種の軸には、概ね、十分なスペースが必
要である。大きいトルクのために大きい継手径を考慮し
なげればならない場合は特に、問題が生ずる。Coupling shafts used in motor vehicles generally have to bridge relatively large distances between, for example, the transmission and the drive shaft. In this case, it is generally also necessary to compensate for height differences and length changes due to varying payloads and spring play during operation. Therefore, the joint must be designed to provide large bend angle and length compensation. The axial structural length of the joint and shaft is thus increased. This type of shaft generally requires sufficient space. Problems arise especially when large joint diameters have to be considered due to large torques.
特殊な事例（例えば、軌道車の駆動装置）では、スペー
ス条件は異なる。多くの場合、継手軸については短い組
込長さが得られるにすぎないが、より大きい継手径は、
スペース問題を生じない。In special cases (eg rail car drives) the space conditions are different. In many cases, only short installation lengths are available for the joint shaft, but larger joint diameters
Does not cause space problems.
この場合、典型的用例は、横形走行エンジンによる車輪
群の駆動である。この場合、運転時の比較的小さい屈曲
角、大きいトルク負荷および荷重時の軸線方向長さ補償
が重要である。自動車製造において慣用の継手軸は上記
要求を満足せず、特に、スプライン軸として構成された
長さ補償部材は、強い摩擦を受け、予想の寿命および確
実性を与えない。公知継手軸によって、短縮は達成され
るが、継手軸受および長さ補償部材の選訳せる構造が弱
い。In this case, a typical application is the drive of a wheel group by a transverse traction engine. In this case, relatively small bending angles during operation, high torque loads and axial length compensation under load are important. The joint shafts customary in automobile manufacturing do not meet the above requirements; in particular, the length compensation elements, which are configured as splined shafts, are subject to strong friction and do not provide the expected service life and reliability. Although shortening is achieved with the known joint shaft, the design of the joint bearing and length compensation member is weak.
本発明の目的は、最大屈曲角が小さく、長さ補償部材が
荷重下でも殆んど抵抗を示さない、永続運転において大
きいトルクに適する短い継手軸を創生ずることにある。The aim of the invention is to create a short joint shaft suitable for high torques in permanent operation, with a small maximum bending angle and in which the length compensation element exhibits almost no resistance under load.
この目的は、請求項第１項に開示の特徴にもとづき、継
手中部が軸線方向へ相互に引離されず、半径方向へテレ
スコピックに配置しである継手構造を選択することによ
って、達成される。継手半部を結合する中間部材は、環
状に構成されており、半径方向内方へ１つの継手半部に
結合され、半径方向外方へ別の継手半部に結合されてい
る。長さ補償部材は、公知の態様で、軸部分およびボス
部分を形状結合状態に相互に結合する転動体を有する三
脚構造に構成されている。This object is achieved according to the features disclosed in claim 1 by selecting a joint construction in which the joint middle parts are not axially separated from each other but are arranged telescopically in the radial direction. The intermediate member connecting the joint halves is of annular design and is connected radially inwardly to one joint half and radially outwardly to another joint half. The length compensation element is constructed in a known manner in a tripod configuration with rolling bodies that interconnect the shaft part and the boss part in a form-fitting manner.
上記の特徴組合せによって、構造長さが特に短い継手軸
が得られる。何故ならば、継手は、軸線方向へ極く僅か
なスペースを必要とするにすぎず、継手軸自体の内部に
部分的に長さ補償部材を配置するスペースを与えるから
である。転動体を使用する長さ補助部材は、同−支持能
のスプライン軸よりも短く構成でき、結合すべき駆動コ
ンポーネント（エンジン、トランスミッション）の軸５
１対する軸線方向反力が小さいと云う利点を有する。The above combination of features results in a joint shaft with a particularly short construction length. This is because the joint requires very little space in the axial direction and provides space for arranging the length compensation element partially inside the joint shaft itself. Length auxiliary members using rolling elements can be constructed shorter than splined shafts of the same supporting capacity and are shorter than the shafts 5 of the drive components (engine, transmission) to be connected.
It has the advantage that the opposing axial reaction force is small.
継手および長さ補助部材の構造長さが短いので、全長が
最小となり、与えられる半径方向スペースが活用される
。Due to the short structural length of the joint and length auxiliary member, the overall length is minimized and the radial space provided is utilized.
本発明の実施例を従属クレームに示した。Embodiments of the invention are set out in the dependent claims.
図面を参照して本発明の実施例を詳細に説明する。Embodiments of the present invention will be described in detail with reference to the drawings.
第１図に、別の駆動コンポーネント（図示してない）に
結合された２つの自在継手１、１１を含む継手軸を示し
た。各継手１、１１は、中間部材３．１３を介して相互
に結合された第１継手半部２．１２および第２継手半部
４，１４から成る。FIG. 1 shows a joint shaft comprising two universal joints 1, 11 connected to further drive components (not shown). Each joint 1, 11 consists of a first joint half 2.12 and a second joint half 4, 14, which are connected to each other via an intermediate member 3.13.
１つの継手１の第２継手半部４は、軸端７を有する中央
軸部分５に移行する。別の継手１１の第２継手半部１４
は、軸端７をパイプ状に囲むボス部分８に移行する。ボ
ス部分８と軸端７との間には、ボルト１０に、好ましく
はころがり軸受によって、軸支し、いっしょに軸端７に
固定したローラ９が設けである。ボス部分８の内面に設
けた軸線方向へ延びるミゾ１５に係合し、形状結合によ
って軸線方向へ可動なよう回転結合を行う３つのローラ
９を設けるのが好ましい。第１継手１に向くボス部分８
の端面には、軸５に沿ってボス部分８を案内する調心ブ
シュ１６が設けである。十分な曲げ強度および静かな走
行に重要なこの調心ブシュは、更に、パツキン１７を有
し、１つの側へのローラ９の摺動の端部ストッパとして
役立つ。ボス部分８の別の側には、別の端部ストッパを
形成し、潤滑剤が流出しないようボス部分８の内部スペ
ースを密閉する蓋２３が設けである。長さ補償部材６は
、中心位置に示してあり、両側へ摺動ストロークａを行
うことができる。The second joint half 4 of one joint 1 transitions into a central shaft part 5 with a shaft end 7 . Second joint half 14 of another joint 11
transitions to a boss portion 8 surrounding the shaft end 7 in a pipe shape. Between the boss part 8 and the shaft end 7 there is provided a roller 9 which is journalled on a bolt 10, preferably by means of rolling bearings, and which is also fixed to the shaft end 7. Preferably, three rollers 9 are provided which engage in axially extending grooves 15 provided on the inner surface of the boss portion 8 and are rotationally coupled to be movable in the axial direction by form-locking. Boss portion 8 facing the first joint 1
An alignment bush 16 is provided on the end face of the shaft 5 for guiding the hub part 8 along the axis 5. This centering bushing, which is important for sufficient bending strength and quiet running, also has a seal 17, which serves as an end stop for the sliding of the roller 9 to one side. On the other side of the boss part 8 there is provided a lid 23 which forms another end stop and seals off the internal space of the boss part 8 against leakage of lubricant. The length compensation member 6 is shown in a central position and can make a sliding stroke a to both sides.
第２図から明らかな如く、軸５は、第２継手半部４とと
もに１つのユニットを形成し、２つの同列の頸軸１８を
有する。上記頸軸は、軸受２０を介して環状中間部材３
１Ｃ結合される。中間部材５は、別の２つの同列の頸軸
１９および軸受２１を介して第１継手半部２に結合され
る。第１図から明らかな如く、軸受２１は、公知の態様
で第１継手半部２に固定された軸受ブロック２２に設け
ることができる。頸軸１８，１９の軸線は、相互に垂直
をなし、１つの平面内にあるのが好ましい。As is clear from FIG. 2, the shaft 5 forms a unit with the second joint half 4 and has two co-aligned neck shafts 18. The neck shaft is connected to the annular intermediate member 3 via a bearing 20.
1C coupled. The intermediate member 5 is connected to the first joint half 2 via two further co-aligned neck shafts 19 and bearings 21 . As is clear from FIG. 1, the bearing 21 can be mounted in a known manner on a bearing block 22 which is fixed to the first joint half 2. The axes of the cervical shafts 18, 19 are preferably mutually perpendicular and lie in one plane.
第３図に１別の自在継手１１のローラ９および軸受の範
囲のボス部分８の断面図を示した。この継手１１の第２
継手半部１４は、ボス部分８から直接に形成され、継手
１と同様に２つの頸軸１８を担持する。環状中間部材１
５による駆動結合は、第２図の継手１の場合と同様であ
る。軸受２０．２１を半径方向外方へ設けたことによっ
て、継手の中心には十分なスペースが得られるので、ボ
ス部分８は、頸軸の軸線の平面までまたは更に第１継手
半部１２まで延ばすことができる。かくして、全構造長
さが明らかに短縮される。第２図から明らかな如く、環
状中間部材３，１３は、楕円形に構成できる。かくして
、軸受２０，２１が回転軸線からほぼ同一の距離を有す
るよう、第１継手半部２．１２の外径を減少できる。回
転角度誤差を避けるため、通常の如く、ボス部分８の頸
軸１８は、軸部分５の頸軸１８と同一の平面に配置する
のが好ましい。軸受２０，２１の潤滑は、注油ニップル
２４を介して行うことができる。FIG. 3 shows a sectional view of the boss part 8 in the area of the rollers 9 and bearings of a further universal joint 11. The second of this joint 11
The joint halves 14 are formed directly from the boss part 8 and, like the joint 1, carry two neck shafts 18. Annular intermediate member 1
The driving connection by 5 is similar to that of joint 1 in FIG. The radially outward arrangement of the bearings 20.21 provides sufficient space in the center of the joint so that the boss part 8 extends into the plane of the axis of the neck shaft or even further into the first joint half 12. be able to. The overall structural length is thus clearly shortened. As is clear from FIG. 2, the annular intermediate members 3, 13 can be constructed in an elliptical shape. The outer diameter of the first joint half 2.12 can thus be reduced so that the bearings 20, 21 have approximately the same distance from the axis of rotation. In order to avoid rotation angle errors, as usual, the neck axis 18 of the boss part 8 is preferably arranged in the same plane as the neck axis 18 of the shaft part 5. Lubrication of the bearings 20, 21 can take place via oil nipples 24.
上述の実施例に、ローラ９を頸軸１０を介して軸端７に
固定した三脚形長さ補償部材６を示した。In the embodiment described above, a tripod-shaped length compensation member 6 is shown, in which a roller 9 is fixed to the shaft end 7 via a neck shaft 10.
この軸構造の場合も、ローラを頸軸な介してボス部分に
固定でき、軸端の縦ミゾによって回転駆動を行うことが
できる。In the case of this shaft structure as well, the roller can be fixed to the boss portion via the neck shaft, and rotationally driven by the vertical groove at the end of the shaft.
第１図は、継手軸受の範囲の継手軸の縦断面図、第２図
は、第１継手の横断面図、第３図は、軸受および転動体
の範囲の第２継手の横断面図である。
１７１１・・・自在継手、２；４；１２；１４・・・継
手半部、３；１３・・・中間部材、５・・・軸部分、６
・・・長さ補償部材、７・・・軸端、８・・・ボス部分
、？・・・転動体
代理人 弁理士 高 野 武 和 賀Figure 1 is a longitudinal cross-sectional view of the joint shaft in the area of the joint bearing, Figure 2 is a cross-sectional view of the first joint, and Figure 3 is a cross-sectional view of the second joint in the area of the bearing and rolling elements. be. 1711... Universal joint, 2; 4; 12; 14... Joint half, 3; 13... Intermediate member, 5... Shaft portion, 6
...Length compensation member, 7...Shaft end, 8...Boss part, ? ...Rolling body agent Patent attorney Takeshi Takano Kazuka
Claims (1)
を介して結合された２つの継手半部（２、４、１２、１
４）からそれぞれ成る２つの自在継手（１、１１）とを
有するテレスコピツク継手軸において、ａ）自在継手（
１、１１）の中間部材（３、１３）の少くとも１つが環
状に構成されており、ｂ）長さ可変の軸部分（５）の中
央軸端（７）およびこの軸端をパイプ状に囲むボス部分
（８）には、三脚形長さ補償部材（６）が設けてあり、
軸端（７）およびボス部分（８）が、転動体（９）を介
して形状結合によつて回転結合されることを特徴とする
継手軸。 ２）転動体（９）が、軸端（７）の半径方向へ向くボル
ト（１０）に軸支されており、ボス部分（８）の軸線平
行のミゾ（１５）内に案内されていることを特徴とする
請求項第１項記載の継手軸。 ３）ボス部分（８）が、軸部分（５）に摺動自在に密封
状態で案内され、調心されていることを特徴とする請求
項第１項記載の継手軸。 ４）ボス部分（８）の外部に対して密封された内部スペ
ースには潤滑剤が充填されていることを特徴とする請求
項第１〜３項の１つに記載の継手軸。 ５）環状中間部材（３、１３）が、半径方向外方へ向く
２つの同列の頸軸（１９）を有し、軸受（２１）を介し
て継手半部（１、２、１１、１２）の１つに結合されて
いることを特徴とする請求項第１〜４項の１つに記載の
継手軸。 ６）環状中間部材（３、１３）の少くとも１つが、半径
方向外方へ延びる２つの相互に同軸の頸軸（１９）と、
−上記頸軸に対して９０゜ずれた−当該継手半部（４、
１４または８）の頸軸（１８）の２つの軸受（２０）を
受容する２つの相互に同軸のボアとを有することを特徴
とするクレーム第１〜４項の１つに記載の継手軸。 ７）環状中間部材（３、１３）が、軸線方向へ見て本質
的に楕円形状を有することを特徴とする請求項第６項記
載の継手軸。 ８）軸部分（５）およびまたはボス部分（８）が、半径
方向外方へ向き軸受（２０）を介して半径方向内方から
環状中間部材に結合された同列の頸軸（１８）を有し、
頸軸（１８および１９）の軸線が相互に垂直をなすこと
を特徴とする請求項第１〜７項の１つに記載の継手軸。 ９）中間部材（３、１３）の頸軸（１８、１９）の軸線
が１つの平面内にあることを特徴とする請求項第８項記
載の継手軸。 １０）ボス部分（８）のミゾ（１５）が、少くとも、半
径方向外方へ向く頸軸（１８）の範囲まで軸線方向へ延
びていることを特徴とする請求項第８項記載の継手軸。 １１）軸受（２１）が、第１継手半部（２、１２）に固
定された軸受ブロツク（２２）によつて囲まれているこ
とを特徴とする請求項第５項記載の継手軸。[Claims] 1) A length-variable shaft portion (5) and an intermediate member (3, 13)
two joint halves (2, 4, 12, 1
4) in a telescopic joint shaft having two universal joints (1, 11) each consisting of: a) a universal joint (
At least one of the intermediate members (3, 13) of 1, 11) is configured in an annular shape, and b) the central shaft end (7) of the length-variable shaft portion (5) and this shaft end are formed into a pipe shape. The surrounding boss portion (8) is provided with a tripod-shaped length compensation member (6),
A joint shaft characterized in that a shaft end (7) and a boss portion (8) are rotationally coupled via a rolling element (9) by form-locking. 2) The rolling element (9) is supported by a radially oriented bolt (10) on the shaft end (7) and guided in a groove (15) parallel to the axis of the boss portion (8). The joint shaft according to claim 1, characterized in that: 3) Coupling shaft according to claim 1, characterized in that the boss part (8) is slidably guided in a sealing manner on the shaft part (5) and is centered. 4) A joint shaft according to one of claims 1 to 3, characterized in that the internal space sealed from the outside of the boss portion (8) is filled with a lubricant. 5) The annular intermediate member (3, 13) has two co-aligned neck shafts (19) pointing radially outwards and connects the joint halves (1, 2, 11, 12) via bearings (21). Joint shaft according to one of claims 1 to 4, characterized in that it is connected to one of the joint shafts. 6) at least one of the annular intermediate members (3, 13) has two mutually coaxial neck axes (19) extending radially outward;
- Misaligned by 90° with respect to the neck axis - The joint half (4,
Joint shaft according to one of claims 1 to 4, characterized in that it has two mutually coaxial bores for receiving two bearings (20) of a neck shaft (18) of 14 or 8). 7) Joint shaft according to claim 6, characterized in that the annular intermediate part (3, 13) has an essentially elliptical shape when viewed in the axial direction. 8) The shaft part (5) and/or the boss part (8) have a co-aligned neck shaft (18) pointing radially outwardly and connected to the annular intermediate member from radially inside via a bearing (20); death,
8. Joint shaft according to claim 1, characterized in that the axes of the neck shafts (18 and 19) are mutually perpendicular. 9) Joint shaft according to claim 8, characterized in that the axes of the neck shafts (18, 19) of the intermediate members (3, 13) lie in one plane. 10) Joint according to claim 8, characterized in that the groove (15) of the boss part (8) extends axially at least to the extent of the neck axis (18) pointing radially outwards. shaft. 11) Joint shaft according to claim 5, characterized in that the bearing (21) is surrounded by a bearing block (22) fixed to the first joint half (2, 12).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3809586.6 | 1988-03-22 | ||
| DE3809586 | 1988-03-22 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH01283434A true JPH01283434A (en) | 1989-11-15 |
Family
ID=6350360
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1060579A Pending JPH01283434A (en) | 1988-03-22 | 1989-03-13 | Telescopic joint shaft |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JPH01283434A (en) |
| DE (1) | DE8816516U1 (en) |
| FR (1) | FR2629156A1 (en) |
| GB (1) | GB2216631B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19529980A1 (en) * | 1995-08-16 | 1997-03-06 | Voith Gmbh J M | Drive element to transmit torque |
| GB2311758A (en) * | 1996-04-04 | 1997-10-08 | Rover Group | A motor vehicle drive shaft assembly |
| DE10106982A1 (en) * | 2001-02-15 | 2002-08-29 | Ina Schaeffler Kg | linear guide |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1923649A (en) * | 1932-10-31 | 1933-08-22 | Universal Products Co Inc | Power transmitting mechanism |
| US2231117A (en) * | 1938-12-15 | 1941-02-11 | Anton F Greiner | Spline joint |
| FR1119680A (en) * | 1953-10-15 | 1956-06-22 | Universal joint | |
| FR2169475A5 (en) * | 1972-01-26 | 1973-09-07 | Glaenzer Spicer Sa | |
| DE2522108A1 (en) * | 1975-05-17 | 1976-11-18 | Voith Getriebe Kg | TELESCOPIC SHAFT |
| DE2809665A1 (en) * | 1978-03-07 | 1979-09-20 | Voith Transmit Gmbh | Universal joint coupling |
| JPS5929151Y2 (en) * | 1980-02-25 | 1984-08-22 | 本田技研工業株式会社 | Slide type constant velocity universal joint |
| FR2498274B1 (en) * | 1981-01-16 | 1986-04-04 | Glaenzer Spicer Sa | TELESCOPIC COUPLING WITH ROLLERS AND ITS APPLICATIONS |
| JPS616431A (en) * | 1984-06-21 | 1986-01-13 | Honda Motor Co Ltd | Propeller shaft |
| JPS61290234A (en) * | 1985-06-17 | 1986-12-20 | Ntn Toyo Bearing Co Ltd | Equal velocity universal joint |
| DE3616209A1 (en) * | 1986-05-14 | 1987-11-19 | Helmut Hartz | PTO SHAFT WITH TWO CARDANO JOINTS |
-
1988
- 1988-03-22 DE DE8816516U patent/DE8816516U1/de not_active Expired - Lifetime
-
1989
- 1989-03-13 JP JP1060579A patent/JPH01283434A/en active Pending
- 1989-03-15 GB GB8905932A patent/GB2216631B/en not_active Expired - Fee Related
- 1989-03-22 FR FR8904332A patent/FR2629156A1/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| GB8905932D0 (en) | 1989-04-26 |
| FR2629156A1 (en) | 1989-09-29 |
| GB2216631A (en) | 1989-10-11 |
| FR2629156B1 (en) | 1995-03-03 |
| DE8816516U1 (en) | 1989-12-14 |
| GB2216631B (en) | 1991-10-02 |
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