GB2311117A - Driveshaft for a motor vehicle driveline - Google Patents

Driveshaft for a motor vehicle driveline Download PDF

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Publication number
GB2311117A
GB2311117A GB9704924A GB9704924A GB2311117A GB 2311117 A GB2311117 A GB 2311117A GB 9704924 A GB9704924 A GB 9704924A GB 9704924 A GB9704924 A GB 9704924A GB 2311117 A GB2311117 A GB 2311117A
Authority
GB
United Kingdom
Prior art keywords
plunging
shaft portion
sliding portion
shaft
driveshaft
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.)
Granted
Application number
GB9704924A
Other versions
GB2311117B (en
GB9704924D0 (en
Inventor
Werner Jacob
Manfred Niderhuefner
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.)
GKN Driveline Deutschland GmbH
Original Assignee
Loehr and Bromkamp GmbH
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 Loehr and Bromkamp GmbH filed Critical Loehr and Bromkamp GmbH
Publication of GB9704924D0 publication Critical patent/GB9704924D0/en
Publication of GB2311117A publication Critical patent/GB2311117A/en
Application granted granted Critical
Publication of GB2311117B publication Critical patent/GB2311117B/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/04—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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/02—Shafts; Axles
    • F16C3/03—Shafts; Axles telescopic
    • F16C3/035—Shafts; Axles telescopic with built-in 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
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/06—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement
    • F16D3/065—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement by means of rolling elements
    • 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
    • F16D3/22—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling 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
    • F16D3/22—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22323—Attachments to the shaft of the inner joint member whereby the attachments are distanced from the core

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Motor Power Transmission Devices (AREA)
  • Arrangement And Driving Of Transmission Devices (AREA)

Description

- c 2311117 c( - Title: DRIVESHAFT FOR MOTOR VEHICLE DRIVELINE
Description of Invention
This invention relates to a driveshaft for a motor vehicle driveline, preferably a halfshaft or sideshaft (herein called a sidesbaft) extending laterally of the vehicle to drive a wheel thereof, the shaft comprising two constant velocity universal joints connected to one another by a connecting shaft which comprises a plunging means and a shaft portion; with the plunging means comprising a plunging journal, a tubular sliding portion which is arranged coaxially around said plunging journal and which is connected to the shaft portion, and rolling contact members which engage tracks associated with the plunging journal and sliding portion and arranged between said plunging journal and sliding portion so as to extend parallel to a longitudinal axis of the connecting shaft; each of the plunging journal and the shaft portion either being integral with a component of one of the constant velocity joints or being connected thereto.
Such a driveshaft is described in DE-4419373-Al for example. The connecting shaft disclosed therein is stiff overall.
When designing driveshafts such as sideshafts for motor vehicles, attempts are usually made to ensure that the connecting shaft, i.e. the shaft arranged between the two constant velocity joints, is designed to match the rotational stiffness of the joints, i.e. to make it as rotationally stiff as possible. However, the effect of such a rotationally stiff design is that, when starting a vehicle violently, i.e. in the case of so-called jump starts, the sudden high loads applied to the constant velocity joints adversely affect their functioning because the load peaks are transmitted in full without any attenuation taking place. In the case of driveshafts, for example, wherein the changes in the length of the driveshaft caused by the jounce and rebound of the wheels are accommodated by constant velocity joints in the form of plunging joints, this may lead to distortion b 1 2 which interferes with the plunging process of the joints adapting to the changed length conditions.
The situation is more advantageous in the case of a driveshaft according to DE-4419373-Al. However, even with such an improved design, the loads on the constant velocity joints are high.
It is an object of the invention to provide a driveshaft wherein, even in the case of high and sudden loads, accurate functioning of the components of the driveshaft is ensured.
In accordance with the invention, in a shaft of the kind herein first set forth, the rotational stiffness of the components constituting the plunging means, i.e. the plunging journal and the sliding portion, is such that when the maximum achievable torque occurs while the wheels of the motor vehicle are driven, the rolling contact members are able to roll freely in the tracks of the plunging journal and sliding portion when a change in length takes place between the two constant velocity joints, and the shaft portion has a lower rotational stiffness than said components of the plunging means.
The advantage of such an embodiment is that sudden loads lead to twistine, of the rotationally less stiff shaft portion. The shaft portion is used as a torsional spring. The acceleration experienced by the vehicle becomes correspondingly softer, which is also regarded as advantageous. The rotational stiffness can be calculated in accordance with the requirements of the vehicle manufacturer in order to achieve the highest possible degree of comfort on the one hand and on the other hand, to ensure that no further driveline components are subjected to impermissibly high loads.
Furthermore, it is advantageous that a plunging bearing is able to keep rotating and vibrating driveshafts quiet and to minimise superimposed stresses. The stiffness of the components of the plunging means is such that the functions of the plunging means are not interfered with. There is a further advantage in that when the shaft portion is subjected to twisting, this does not affect the joints 3 because the change in length caused by twisting is offset by the plunging means. The adjacent joints are not subjected to any loads.
According to a preferred embodiment, the components of the plunging means may be assembled relative to one another under a preload.
Accordingly, the rotational stiffness of the shaft portion is calculated to be such that there is a predetermined rotational stiffness adapted to the vehicle.
A particularly advantageous embodiment is achieved if the shaft portion, with the exception of two connecting end regions, is cylindrical and solid, i.e. not hollow. However, it is alternatively proposed that the shaft portion may be produced so as to be integral with the sliding portion, that the sliding portion may be of tubular form with a corrugated cross-section, and that the shaft portion may be provided in the form of a cylindrical tube portion.
If a solid configuration is selected for the shaft portion, it is proposed that the diameter of a connecting region of the shaft portion, provided towards the sliding portion of the plunging means, may be increased by making such connecting region of dished or cup-like configuration. Tle sliding portion of the plunging means is fixed to said connecting region; it may be fixed by welding for example.
Preferred embodiments of the invention, and its application to a fourwheel drive motor vehicle, are diagrammatically illustrated in the drawings and explained in greater detail with reference thereto.
Figure 1 shows the overall drive arrangement of a four-wheel drive vehicle; Figure 2 is a longitudinal section through a first embodiment of a driveshaft in accordance with the invention; Figure 3 is a modified embodiment of the connecting shaft, with the shaft portion made of a solid material being shown with the connected sliding portion in the form of a deep drawn part; 4 Figure 4 is a modified embodiment of a driveshaft wherein the sliding portion and the shaft portion are produced in one place in the form of a tube.
In the following description, parts of the different embodiments, corresponding to one another in function are identified by the same reference numerals but with an additional prime(') or double prime (11).
Figure 1 shows a four-wheel drive vehicle with a driveline, having an engine 3 and manual gearbox driving a front axle differential 4 from the outputs of which the two front wheels 1 are drivable via sideshafts 7. Drive for the rear wheels 2 is derived from the front axle differential 4, so that a rear axle differential 5 is driven by a distributor drive and a propeller shaft, and sideshafts 6 extend from the rear axle differential 6 to the rear wheels 2.
Figure 2, in the form of a longitudinal section, shows a first embodiment of a shaft such as a sideshaft 6 for driving one of the two rear wheels 2 for example.
The driveshaft 6 according to Figure 2, which is intended to be used as a sideshaft, comprises two constant velocity joints, i.e. a first constant velocity joint 3 arranged at the end of the shaft adjacent the rear wheel and a second constant velocity joint arranged at the end of the shaft adjacent the axle differential. The two constant velocity joints 8, 9 are connected to one another by a connecting shaft 10. The first constant velocity joint 8 comprises an hollow outer joint part 11 which, in its cavity, is provided with outer running grooves 12 which are spaced around the longitudinal axis 22. For connecting the outer joint part 11 to the wheel hub of one of the rear wheels, there is provided a connecting journal 13. In the cavity of the outer joint part 11, an inner joint part 14, with the help of a control element 21, is supported so as to be pivotable in all directions. On its outer face, the inner joint part 14 comprises inner running grooves 15 which are arranged opposite the outer running grooves 12 of the outer joint part 11. Each pair of opposed outer running grooves 12 and inner running grooves 15 accommodates a respective ball 17 for torque transmitting purposes. The balls 17 are guided in windows of a cage 16. The inner joint part 14 carries a connecting journal 18 which extends towards the second constant velocity joint 9 and which, at its end, is provided with connecting means- 19 to be attached to corresponding connecting means of a shaft portion 33 of the connecting shaft 10. The space between the connecting journal 18 and the outer joint part 11 is sealed by a boot 20. In principle, the second constant velocity joint 9 is similar to the first constant velocity joint 8; only its connecting means are different.
The inner joint part 23 of the second constant velocity joint 9 carries a plunging journal 24 which forms part of a plunging assembly 25. The outer face of the plunging journal 24 is provided with running grooves 26 for rolling contact members 27, which running grooves 26 are circumferentially distributed around the longitudinal axis 22 and extend along same. The rolling contact members 27 are preferably in the form of balls, with a plurality of such balls being arranged one behind the other in each running groove 26. The rolling contact members 27 are held in a cage 28. They also engage running grooves 30 of a sliding portion 29, which is in the form of a tubular component. The running grooves 30 are arranged opposite the running grooves 26 and also extend parallel to the longitudinal axis 22. Between the outer face of the sliding portion 29 and that of the outer joint part of the constant velocity joint 9, there is attached a boot 34 for sealing. A cap 31 is inserted into the bore of the sliding portion 29 so as to extend towards the shaft portion 33 of the connecting shaft 10. The cap 31 limits the adjustment path of the rolling contact members 27 in the running grooves 26, 30.
The components of the plunging assembly are preferably assembled to one another under a preload in respect of the engagement of the rolling contact members in the grooves 26,30, so that in use rolling contact conditions are assured therebetween and radial and circumferential play is prevented from developing.
The connecting end of the sliding portion 29, which connecting end faces the shaft portion 33, is joined by welding to a connecting region of the shaft portion 33, which connecting region is dished or cup-shaped in form. At its other 0 6 end, the shaft portion 33 is provided with connecting means 32 to be connected to the connecting means 19 of the connecting journal 18 of the constant velocity joint 8, said connecting journal 18 being associated with the inner joint part 14. The shaft portion 33 is of solid (non- hollow) configuration and is cylindrical in shape. The rotational stiffness of the plunging assembly 25 or rather of the components of same, i.e. of the sliding portion 29 and the plunging journal 24, is calculated in such a way that when the maximum torque is transmitted, and also in the case of violent or so-called jump starts, the plunging function is ensured, i.e. the rolling contact members 27 in the running grooves 26, 30 are able to roll accurately to be able to accommodate, in an interference-free way, any changes in length between the centres of the constant velocity joints 8, 9. The rotational stiffness of the shaft portion 33 is correspondingly lower, so that in the case of certain torque loads, any twisting in the shaft portion 33 takes place in the elastic range. The above described measures make it impossible, in the case of changes in length caused by twisting, for any forces which would result in distortion to be applied to the constant velocity joints 8, 9 connected to the connecting shaft 10.
Figure 3 shows part of an embodiment modified in respect of the shaft portion 33 ' and the sliding portion 29 ' connected thereto. It can be seen that, in contrast to the embodiment according to Figure 2, the sliding portion 29 ' is provided in the form of a deep drawn part and that the cross-section has a corrugated shape. The corrugated shape, the provision of indentations in the tubular portion of the sliding portion 29 ', results in a high rotational stiffness, so that, under torque, there occurs practically no deformation or only slight deformation, and it is thus ensured that the rolling contact members roll.accurately in the valleys of the sliding portion 29 '. It can be seen that the sliding portion 29 ', towards the connecting region 35 of the shaft portion 33 ', comprises a collar which is drawn inwardly. The central opening is closed by a plug. The connecting region 35 is formed by a dished or cup-shaped enlargement of the diameter of the shaft portion 33 ' of solid form. The sliding portion 29' is joined to the connecting region 35 by a weld 36. At the end facing away from 7 the sliding portion 29 ', there can be seen connecting means 32 which are formed by end teeth which are provided at a collar formed on to the shaft portion 33 ' Figure 4 shows an embodiment of a driveshaft 6 ' wherein the sliding portion 29 11 associated with the connecting shaft 10 ' and the shaft portion 33 ' are produced in one piece from a tube, with the tube being extending towards the sliding portion 29 0. In this region, it has a rotational stiffness which is calculated in such a way that even in the case of high and sudden torque loads, there cannot occur any deformation which would be high enough adversely to affect the functioning of the plunging assembly 25 ', i.e. which would hinder changes in length between the two constant velocity joints 8 ' and 9 '. The connection between the inner joint part of the constant velocity joint 8 ' and the tubular shaft portion 33 11 whose diameter is reduced relative to the sliding portion 29 11 is established by a short journal 18 ' whose outer face may be provided with teeth which extend along the longitudinal axis 22 and which are pressed into the bore of the shaft portion 33 ",, thus establishing a close connection. Axial security may be provided by a securing ring. The rotational stiffness of the tubular shaft portion 33 11 is also based on the criteria as described in connection with the embodiment of Figure 2.
The features disclosed in the foregoing description, or the following claims, or the accompanying drawings, expressed in their specific forms or in terms of a means for performing the disclosed function, or a method or process for attaining the disclosed result, as appropriate, may, separately or in any combination of such features, be utilised for. realising the invention in diverse forms thereof.
8

Claims (7)

CIAIMS
1. A driveshaft for a motor vehicle driveline, the shaft comprising two constant velocity universal joints connected to one another by a connecting shaft which comprises a plunging means and a shaft portion; with the plunging means comprising a plunging journal, a tubular sliding portion which is arranged coaxially around said plunging journal and which is connected to the shaft portion, and rolling contact members which engage tracks associated with the plunging journal and sliding portion and arranged between said plunging journal and sliding portion so as to extend parallel to a longitudinal axis of the connecting shaft; each of the plunging journal and the shaft portion either being integral with a component of one of the constant velocity joints or being connected thereto; wherein the rotational stiffness of the components constituting the plunging means is such that when the maximum achievable torque occurs while the wheels of the motor vehicle are driven, the rolling contact members are able to roll freely in the tracks of the plunging journal and sliding portion when a change in length takes place between the two constant velocity joints, and the shaft portion has a lower rotational stiffness than said components of the plunging means.
2. A driveshaft according to Claim 1 wherein said components of the plunging means are assembled relative to one another under a preload.
3. A driveshaft according to Claim 1 or Claim 2 wherein, with the exception of connecting end regions thereof, the shaft portion is cylindrical and solid.
4. A driveshaft according to Claim 1 or Claim 2 wherein said shaft portion is integral with the sliding portion and the sliding portion is of tubular form with a corrugated cross-section, the shaft portion being of cylindrical tubular form.
9
5. A driveshaft according to Claim 3 wherein the diameter of a connecting end region of the shaft portion, provided towards the sliding portion of the plunging means, is increased in a dished or cup-like configuration.
6. A driveshaft substantially as hereinbefore described with reference to Figure 2, 3 or 4 of the accompanying drawings.
7. Any novel feature or novel combination of features described herein and/or in the accompanying drawings.
GB9704924A 1996-03-11 1997-03-10 Driveshaft for motor vehicle driveline Expired - Lifetime GB2311117B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE1996109423 DE19609423C2 (en) 1996-03-11 1996-03-11 Cardan shaft, in particular a side shaft for driving the wheels of a motor vehicle

Publications (3)

Publication Number Publication Date
GB9704924D0 GB9704924D0 (en) 1997-04-30
GB2311117A true GB2311117A (en) 1997-09-17
GB2311117B GB2311117B (en) 1998-04-15

Family

ID=7787890

Family Applications (1)

Application Number Title Priority Date Filing Date
GB9704924A Expired - Lifetime GB2311117B (en) 1996-03-11 1997-03-10 Driveshaft for motor vehicle driveline

Country Status (6)

Country Link
JP (1) JPH10955A (en)
CN (1) CN1087239C (en)
BR (1) BR9701249A (en)
DE (1) DE19609423C2 (en)
FR (1) FR2745761B1 (en)
GB (1) GB2311117B (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2339461A (en) * 1998-07-10 2000-01-26 Gkn Loebro Gmbh Propeller shaft assembly
GB2339463A (en) * 1998-07-10 2000-01-26 Gkn Loebro Gmbh Constant velocity drive assembly with damper on flange.
GB2339465A (en) * 1998-07-10 2000-01-26 Gkn Loebro Gmbh Drive assembly
GB2344403A (en) * 1998-12-05 2000-06-07 Gkn Loebro Gmbh Telescopic shaft
GB2347729A (en) * 1999-03-12 2000-09-13 Gkn Loebro Gmbh Constant velocity joint and plunging shaft assembly.

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DE19756768C2 (en) * 1997-12-19 2003-03-27 Gkn Loebro Gmbh CV shaft with two fixed joints and separate displacement
DE10158544C2 (en) * 2001-11-29 2003-10-30 Gkn Loebro Gmbh Longitudinal displacement unit made of material of the same wall thickness
DE112004001172D2 (en) 2004-10-29 2006-08-24 Gkn Driveline Int Gmbh Longitudinal displacement unit with axial postioning of the cage
WO2008107288A1 (en) * 2007-03-02 2008-09-12 Schaeffler Kg Fixed constant-velocity joint, transmission device comprising the fixed constant-velocity joint and method for producing the fixed constant-velocity joint
DE102010009685B4 (en) * 2009-03-02 2017-10-19 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Constant velocity joint
DE202009006696U1 (en) 2009-05-08 2010-09-23 Bf New Technologies Gmbh Constant velocity joint and propeller shaft
KR101451155B1 (en) * 2013-10-11 2014-10-15 현대자동차주식회사 Mounting structure of Drive-shaft
JP6209108B2 (en) * 2014-03-12 2017-10-04 本田技研工業株式会社 Universal joint
CN105715689A (en) * 2016-04-12 2016-06-29 力帆实业(集团)股份有限公司 Automobile and connecting structure for automobile transmission shaft and differential mechanism
WO2018196960A1 (en) * 2017-04-25 2018-11-01 Gkn Driveline Deutschland Gmbh Shaft connection and input shaft having a shaft connection of this kind
CN110614880B (en) * 2019-10-25 2020-12-15 合肥海源机械有限公司 Flexible transmission new energy electric special vehicle drive axle and use method thereof
CN113323969B (en) * 2021-06-28 2022-05-17 斯捷尔传动机械(杭州)有限公司 Flexible agricultural machine transmission shaft with high-precision constant-velocity joint assembly and manufacturing method thereof

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GB1538546A (en) * 1975-07-22 1979-01-24 Walterscheid Gmbh Jean Transmission shaft
US4540385A (en) * 1982-10-22 1985-09-10 Uni-Cardan Aktiengesellschaft Drive shaft assembly
US5611733A (en) * 1994-06-03 1997-03-18 Lohr & Bromkamp Gmbh Driveshaft with plunging part

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Publication number Priority date Publication date Assignee Title
GB501171A (en) * 1937-01-14 1939-02-22 Paul Charles Albert Marie D Au Improvements in power transmission couplings
GB944679A (en) * 1961-03-07 1963-12-18 Rheinmetall Gmbh Improvements in or relating to shafts, more particularly universal joint shafts, with torsional flexibility
GB1538546A (en) * 1975-07-22 1979-01-24 Walterscheid Gmbh Jean Transmission shaft
US4540385A (en) * 1982-10-22 1985-09-10 Uni-Cardan Aktiengesellschaft Drive shaft assembly
US5611733A (en) * 1994-06-03 1997-03-18 Lohr & Bromkamp Gmbh Driveshaft with plunging part

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6241617B1 (en) 1998-07-10 2001-06-05 Gkn Lobro Gmbh Propeller shaft assembly for a motor vehicle especially a passenger car
GB2339465B (en) * 1998-07-10 2000-08-02 Gkn Loebro Gmbh Drive assembly
US6251021B1 (en) 1998-07-10 2001-06-26 Gkn Lobro Gmbh Drive assembly with a constant velocity fixed joint and a damping element
GB2339461A (en) * 1998-07-10 2000-01-26 Gkn Loebro Gmbh Propeller shaft assembly
GB2339463B (en) * 1998-07-10 2001-03-14 Gkn Loebro Gmbh Drive assembly
GB2339461B (en) * 1998-07-10 2000-08-02 Gkn Loebro Gmbh Propeller shaft assembly
US6234908B1 (en) 1998-07-10 2001-05-22 Gkn Lobro Gmbh Drive assembly with at least one constant velocity fixed joint having a set of rolling contact member guiding means
GB2339463A (en) * 1998-07-10 2000-01-26 Gkn Loebro Gmbh Constant velocity drive assembly with damper on flange.
GB2339465A (en) * 1998-07-10 2000-01-26 Gkn Loebro Gmbh Drive assembly
US6217456B1 (en) 1998-12-05 2001-04-17 Gkn Lobro Gmbh Telescopic shaft
GB2344403B (en) * 1998-12-05 2000-11-29 Gkn Loebro Gmbh Telescopic shaft
GB2344403A (en) * 1998-12-05 2000-06-07 Gkn Loebro Gmbh Telescopic shaft
ES2160527A1 (en) * 1998-12-05 2001-11-01 Gkn Loebro Gmbh Telescopic shaft
GB2347729A (en) * 1999-03-12 2000-09-13 Gkn Loebro Gmbh Constant velocity joint and plunging shaft assembly.
GB2347729B (en) * 1999-03-12 2001-03-14 Gkn Loebro Gmbh Assembly having a constant velocity fixed joint with a connecting shaft
US6306045B1 (en) 1999-03-12 2001-10-23 Gkn Lobro Gmbh Assembly having a constant velocity fixed joint and a connecting shaft
ES2160526A1 (en) * 1999-03-12 2001-11-01 Gkn Loebro Gmbh Assembly having a constant velocity fixed joint and a connecting shaft

Also Published As

Publication number Publication date
CN1087239C (en) 2002-07-10
BR9701249A (en) 1998-11-10
CN1167054A (en) 1997-12-10
DE19609423C2 (en) 2000-07-27
JPH10955A (en) 1998-01-06
DE19609423A1 (en) 1997-09-18
FR2745761B1 (en) 2001-04-13
FR2745761A1 (en) 1997-09-12
GB2311117B (en) 1998-04-15
GB9704924D0 (en) 1997-04-30

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