WO2006048029A1 - Längsverschiebeeinheit mit axialer positionierung des käfigs - Google Patents
Längsverschiebeeinheit mit axialer positionierung des käfigs Download PDFInfo
- Publication number
- WO2006048029A1 WO2006048029A1 PCT/EP2004/012312 EP2004012312W WO2006048029A1 WO 2006048029 A1 WO2006048029 A1 WO 2006048029A1 EP 2004012312 W EP2004012312 W EP 2004012312W WO 2006048029 A1 WO2006048029 A1 WO 2006048029A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- longitudinal displacement
- displacement unit
- profiled
- unit according
- spring
- Prior art date
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
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/306—Means to synchronise movements
-
- 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
Definitions
- the invention relates to a longitudinal displacement unit for torque transmission zwi ⁇ rule two relatively axially displaceable parts, comprising a profiled tap with first circumferentially distributed longitudinal ball grooves, a profile sleeve with second circumferentially distributed longitudinal ball grooves, balls which are arranged in pairs of first and second ball grooves in groups , And a Kugelhan ⁇ fig, which lies between the profile pin and profile sleeve and the balls fixed in position relative to each other.
- Such longitudinal displacement units are used, in particular, in drive shafts in the drive train of a motor vehicle, as are known, for example, from DE 196 09 423 A1.
- a rei ⁇ low-yielding length compensation must be made possible under torque load.
- a longitudinal displacement unit for transmitting a torque which identifies a plurality of rows of balls arranged in a ball cage, wherein the balls of a row of balls consist of elastic material and are biased radially in the associated ball grooves.
- US 6 343 993 B1 shows a similar longitudinal displacement unit in which the balls are radially biased by elastic elements.
- a longitudinal displacement unit for Dreh ⁇ torque transmission in a drive assembly comprising a profile sleeve with circumferentially distributed longitudinal first ball grooves; a profiled pin having circumferentially distributed longitudinally extending second ball grooves; Balls arranged in pairs in pairs of first and second ball grooves; a cure gelhanfig which is arranged between the profile sleeve and the profiled pin and fixes the balls in position relative to each other; and spring means which are supported on at least ei ⁇ nem axial stop and are designed such that the ball cage is held in an unloaded state at a distance from the at least one axial stop.
- the Fede rstoff a first spring, which is arranged between the ball cage and the at least one Aocialanschlag.
- the use of only one spring is particularly advantageous in applications in which the cage migration occurs only in one direction.
- the spring means may also comprise a second spring which is supported on a second axial stop, wherein the first axial stop and the second axial stop are arranged on opposite sides of the ball cage. This ensures that the ball cage can be acted upon axially from both sides and held in a middle working position.
- both the first and the second axial stop are formed on the profiled journal.
- the first and the second axial stop can also be formed on the profile sleeve.
- the first axial stop is associated with the profiled pin and the second axial stop is associated with the profiled sleeve.
- the axial stop assigned to the profiled tap is preferably arranged at the end which dips into the profiled sleeve.
- the axial stop assigned to the profile sleeve is preferably arranged at the opening-side end.
- This embodiment with the axial stop associated with the profiled pin on the shaft side and the opening on the side of the profiled sleeve assigned to the axial end stop, has the effect that a pull-out stop for the profiled pin is formed in relation to the profiled sleeve.
- the profiled pin is supported in a pulled-out position over the first axial stop, the first spring, the ball cage and the second spring against the second axial stop>. Unintentional sliding out of the profiled journal from the profiled sleeve, for example during assembly, is thereby prevented.
- the at least one axial stop is designed in the form of a securing ring, which is axially fi xed on the profiled sleeve or the profiled hub. This can be done for example by means of a locking ring which engages in a corresponding annular groove. It is advantageous here to introduce the annular groove in a region outside the ball grooves in order to be able to carry out the turning operation in a non-interrupted section.
- at least one of the first and second axial stops can also be designed in the form of a stop sleeve, which is axially supported relative to the profile sleeve or the profiled pin.
- first and the second spring are biased. This prevents that the ball cage loosely between tween the springs due to vibrations. Rather, the ball cage is held at a defined working position.
- the first and second springs may be different or the same length.
- An equal length of the springs has the advantage that the ball cage is held symmetrically between the two axial stops. A different length of the springs is advantageous in certain applications in which an unsymmetrical position is desired.
- the first and / or the second spring are preferably designed in the form of coil springs, which can be produced easily and cost effectively.
- the first and the second spring have a largest outer diameter, which is smaller than a smallest inner diameter of the profile sleeve in the region of the ball grooves. Furthermore, the first and the second Fe ⁇ have a smallest inner diameter which is greater than a largest réelle trim ⁇ diameter of the profiled pin in the ball grooves.
- the first and / or the second springs may be arranged loosely between the ball cage and the axial stops or, alternatively, be fixedly connected to the ball cage.
- a lying in a common radial plane group of balls have a larger diameter than the balls of übri ⁇ gene groups.
- the play between the profile journal and the profile sleeve is minimized or a slight pressure is generated which prevents the cage cage from walking.
- ange ⁇ rdnet wherein the ball grooves of the other of the two sliding parts regularly distributed over the circumference are.
- FIG. 1 shows a longitudinal displacement unit according to the invention in a longitudinal section according to ei ⁇ ner first embodiment
- FIG. 2 shows a longitudinal displacement unit according to the invention in a longitudinal section according to a second embodiment
- FIG. 3 shows a longitudinal displacement according to the invention in longitudinal section according to a third embodiment
- FIG. 4 shows a longitudinal displacement according to the invention in longitudinal section according to a fourth embodiment
- FIG. 5 shows a L Lucassverschiebeei beauty according to the invention in longitudinal section after ei ⁇ ner fifth embodiment
- FIG. 6 shows a longitudinal displacement unit according to the invention in a longitudinal section according to a sixth embodiment
- FIG. 7 shows a longitudinal displacement unit according to the invention in a longitudinal section according to a seventh embodiment
- Figure 8 shows the profiled pin of a longitudinal displacement unit according to the invention according to an eighth embodiment
- FIG. 9 shows the ball cage of a longitudinal displacement unit according to the invention according to a ninth embodiment
- FIGS. 1 to 7 will be described together first.
- a longitudinal displacement unit for torque transmission for a shaft arrangement which comprises a profiled journal 11 with first ball grooves 12 and a profile sleeve 21 with second ball grooves 22.
- the ball grooves 12, 22 are arranged in a matching circumferential position, wherein the number of the first ball grooves 12 may be a multiple of 10 times the number of the second ball grooves 22.
- opposing first and second ball grooves 12, 22 carry balls 31 which are arranged in groups and which are held by a sleeve-shaped ball cage 41 in a reliable manner in mutually identical axial arrangement.
- the profiled pin 11 has a connection side 13 with a shaft toothing 14 for transmitting torque to a not shown inner joint part of a constant velocity joint.
- the inner joint part by means of a locking ring which engages in a-annular groove 15 on the connection side 13 ,. axially fixed.
- the profile sleeve 2.1. has an opening 23 into which the profiled pin 11 is inserted with a shaft-side end 16 ein ⁇ . In the opening 23, a retaining ring 27 is inserted into a corresponding ring groove, against which the ball cage 41 when pulling out of the profiled pin 11 from the profile sleeve 21 can start indirectly.
- the profile sleeve 21 has a connection side 24 with a shaft toothing 25 for non-rotatable attachment of a constant velocity joint, not shown here. This is axially fixed by means of a securing ring, which engages in the annular groove 26.
- spring means 51 are provided which hold the ball cage 41 in a central position.
- the spring means 51 according to the Ausry ⁇ insurance forms of Figure 1 to 5 comprise a first spring 52 which is arranged such that a movement of the ball cage 41 in the direction of connection side 24 of the Profil ⁇ sleeve 21 is decelerated, and a second spring 53, the like is arranged, that a movement of the ball cage 41 in the direction of the connection side 13 of the Profilzap ⁇ fens 11 is braked.
- the two springs 52, 53 are designed in the form of fferenfe ⁇ countries. The radial dimensions are chosen so that the springs 52, 53 with radial clearance between the profile sleeve 21 and the profiled pin 11 and thus are axially free to move.
- FIG. 1 shows a longitudinal displacement unit with a first axial stop 42, which is assigned to the profile sleeve 21, and with a second axial stop 43, which is assigned to the profiled pin 11.
- the first axial stop 42 is designed in the form of a stop sleeve 44, which is inserted into the profile sleeve 11 and engages positively in the ball grooves 12.
- the profiled sleeve 44 is configured in such a way that the profiled pin 11 can pass through its end 16 when retracted, while the spring 52 starts against the profiled sleeve 44.
- the spring 52 is supported against the stop sleeve 44 and urges the ball cage 41 in the direction of the opening 23.
- the second axial stop 43 against which the second spring 53 is axially supported, is formed by a ring collar which increases the diameter of the profile pin 45 formed.
- the outer diameter of the annular collar 45 is greater than the inner diameter of the second spring 43.
- the spring 43 runs against the annular collar 45 axially and urges the ball cage 41 in Direction Wellen workedem end 16.
- the annular collar of the second Axial ⁇ stop 43 could also be designed by a securing ring which engages in a corre sponding annular groove of the profiled pin.
- the ball cage 41 is held symmetrically between the two axial stops 42, 43 during operation in a middle position.
- the lengths of the springs 52, 53 in relation to the distance of the axial stops 42, 43 to the ball cage 41 are designed such that the springs 52, 53 are prestressed in the assembled state and act upon the ball cage 41 in the middle position.
- FIG. 2 shows a similar embodiment as Figure 1.
- both springs 52, 53 are axially supported relative to the profile sleeve 21.
- the ball cage 41 is held asymmetrically between the two axial stops 42, 43. This is achieved in that the first spring 52 assigned to the shaft-side end 16 is longer than the second spring 53 assigned to the connection-side end 13.
- the first axial stop 42, against which the first spring 52 is axially supported, is formed by the stop sleeve 44. which is inserted into the profile sleeve 21.
- the profiled pin 11 can dip through the first spring 52.
- the second axial stop 43, against which the connection-side second spring 53 is axially supported, is formed by the retaining ring 27 axially fixed in the profile sleeve 21.
- the ball cage 41 is supported axially only relative to the profile sleeve 21, while the profiled pin 11 is freely displaceable relative to the springs 52, 53.
- the lengths of the springs 52, 53 in relation to Ab ⁇ stood the axial stops 42, 43 to the ball cage 41 designed so that the springs 52, 53 are biased in the assembled state and act on the ball cage 41 from both sides. Due to the unequal length of the springs 52, 53, the ball cage 41, in relation to the axial stops 42, 43, assumes an eccentric position during normal operation.
- the lengths of the springs 52, 53 are designed so that the ball cage 41 is held in the operating state in the desired position.
- the embodiment of Figure 3 largely corresponds to that of Figure 2, to the description of which reference is made.
- the springs 52, 53 in the present embodiment have the same length, so that the ball cage 41 is held symmetrically in the middle between the two axial stops 42, 43.
- the springs 52, 53 are not biased in the assembled state in the present embodiment.
- the entire axial length of the springs 52, 53 is shorter than the distances between the axial stops 42, 43 and the Kugelhan ⁇ fig 41.
- the springs 52, 53 thus lie loosely between the axial stops 42, 43 and the ball cage 41.
- Both axial stops 42, 43 are associated with the profile sleeve 21.
- the embodiment according to FIG. 5 is characterized in that the first axial stop 42 is assigned to the profiled pin 11, while the second axial stop 43 is assigned to the profiled sleeve 21.
- the first axial stop 42 for the first spring 52 is formed by a securing ring 28 which engages at the shaft-side end 16 of the profiled pin 11 in a corre sponding annular groove.
- the second axial stop 43 for the second spring 53 is formed by a securing ring 27 which engages at the opening end 23 in a corresponding annular groove of the profile sleeve 21.
- the particular of the present embodiment is that only a single spring 52 is used, which is arranged between the axial stop 42 and the ball cage 41. This has the advantage of a more favorable production and assembly, as it is possible to dispense with a component.
- the embodiment with only one spring 52 is particularly useful when a migration of the Ku ⁇ gelharifigs 41 occurs due to vibrations only in an axial direction.
- the installation state of the longitudinal displacement unit is such that the ball cage 41 merely travels in the direction of the shaft soapy end 16, whereby the ball cage 41 can be axially supported on the stop sleeve 44 by the spring 52 in the interior of the profile sleeve 21 ,
- the spring 52 may loosely between the axial stop 42 and the ball cage 41 einitzen or be verbund s with the ball cage 41.
- the length of the spring 52 is selected so that the ball cage 41 is held in the operating position in the desired position.
- FIG. 7 shows a similar embodiment whose construction and mode of operation substantially correspond to the embodiment according to FIG. The description thereof is referred to insofar, wherein the same components are provided with the same reference numerals.
- the spring 53 is arranged on the opening side.
- the spring is arranged between the ball cage 41 and an axial stop 43 in the form of a securing ring 27.
- the installation state of the Leksverschie ⁇ unit is such that the ball cage 41 moves only in the direction of the opening end 23, wherein the ball cage 41 via the spring 53 on the Siche ⁇ insurance ring 27 axially support -kann. - - - -. ,
- FIG. 8 shows a profiled journal 11 'from which a ball groove 12' is arranged outside a regular circumferential distribution of the remaining ball grooves 12. It is provided that the ball grooves 22 of the outer profile sleeve 21st regularly distributed over the circumference. Due to the deliberate slight pitch error of a ball groove 12 ', the associated balls 31 are installed with slight pressure. Due to the greater pressure, a displacement of the ball cage 41 in addition to the spring means is prevented. As an alternative to the embodiment shown, a ball groove of the profile sleeve could also be arranged outside a regular circumferential distribution of the remaining outer ball grooves. In this case, the inner ball grooves of the profiled pin would then be regularly distributed over the circumference.
- FIG. 9 shows a ball cage 41 with balls 31, a group of balls 31 'located in a common radial plane having a slightly larger diameter than the balls 31 of the remaining groups.
- a small axial displacement resistance is generated on the ball cage 41, which remains effective even in the case of complete freedom from torque and thus the relief of the torque-transmitting balls 31.
- the friction generated by the balls 31 'of larger diameter is so small that the displacement resistance of the longitudinal displacement unit is not appreciably increased under torque.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Springs (AREA)
- Motor Power Transmission Devices (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112004001172T DE112004001172D2 (de) | 2004-10-29 | 2004-10-29 | Längsverschiebeeinheit mit axialer Postionierung des Käfigs |
PCT/EP2004/012312 WO2006048029A1 (de) | 2004-10-29 | 2004-10-29 | Längsverschiebeeinheit mit axialer positionierung des käfigs |
US10/562,429 US20070021223A1 (en) | 2004-10-29 | 2004-10-29 | Longitudinal plunging unit permitting axial positioning of the cage |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP2004/012312 WO2006048029A1 (de) | 2004-10-29 | 2004-10-29 | Längsverschiebeeinheit mit axialer positionierung des käfigs |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006048029A1 true WO2006048029A1 (de) | 2006-05-11 |
Family
ID=34959233
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2004/012312 WO2006048029A1 (de) | 2004-10-29 | 2004-10-29 | Längsverschiebeeinheit mit axialer positionierung des käfigs |
Country Status (3)
Country | Link |
---|---|
US (1) | US20070021223A1 (de) |
DE (1) | DE112004001172D2 (de) |
WO (1) | WO2006048029A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1956252A1 (de) | 2007-02-09 | 2008-08-13 | Spicer Gelenkwellenbau GmbH | Längsverschiebeeinheit für Gelenkwellen |
CN107208690A (zh) * | 2015-02-16 | 2017-09-26 | 罗伯特博世汽车转向有限公司 | 用于机动车的转向中间轴以及用于运行用于机动车的转向中间轴的方法 |
WO2019220053A1 (fr) * | 2018-05-15 | 2019-11-21 | Safran Aircraft Engines | Dispositif de transmission de couple a frottements reduits |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
BRPI0814390A2 (pt) * | 2007-07-26 | 2019-09-24 | Bf New Tech Gmbh | unidade de rolamento-deslizante e eixo articulado que compreende a mesma |
EP2166239B1 (de) | 2008-09-18 | 2012-04-18 | Centa-Antriebe Kirschey GmbH | Wellenanordnung zur Drehmomentübertragung |
WO2019050053A1 (ko) * | 2017-09-05 | 2019-03-14 | 이래에이엠에스 주식회사 | 드라이브 샤프트의 플런징 어셈블리 및 이를 포함하는 드라이브 샤프트 |
US11407439B2 (en) * | 2019-04-08 | 2022-08-09 | Steering Solutions Ip Holding Corporation | Steering shaft assembly |
KR200496987Y1 (ko) * | 2021-05-11 | 2023-06-28 | 주식회사 고려농기 | 농기계 유니버설 조인트용 고정핀 |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1800996U (de) | 1959-05-12 | 1959-11-26 | Wolfgang Grauff | Kugelgeradfuehrung. |
FR1373752A (fr) * | 1963-08-12 | 1964-10-02 | Glaenzer Spicer Sa | Dispositif de coulissement pour transmission d'un couple, à corps de roulement et ressorts de localisation de ces derniers |
DE2532661A1 (de) * | 1975-07-22 | 1977-01-27 | Walterscheid Gmbh Jean | Teleskopwelle, insbesondere fuer landmaschinen |
EP0189011A2 (de) | 1985-01-22 | 1986-07-30 | Affärsverket FFV | Teleskopische Welle insbesondere zur Drehmomentübertragung |
DE3940488A1 (de) * | 1989-12-07 | 1991-06-13 | Schaeffler Waelzlager Kg | Kugellaengsfuehrung, insbesondere fuer teleskopantriebswellen |
DE19609423A1 (de) | 1996-03-11 | 1997-09-18 | Loehr & Bromkamp Gmbh | Gelenkwelle, insbesondere Seitenwelle zum Antrieb der Räder eines Kraftfahrzeuges |
US6343993B1 (en) | 1999-06-30 | 2002-02-05 | Nacam France S.A. | Ball-type system for coupling two sliding shafts |
DE10233758A1 (de) | 2002-07-25 | 2004-03-11 | GKN Löbro GmbH | Längsverschiebeeinheit mit Bremsrollen |
Family Cites Families (10)
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US2833598A (en) * | 1954-03-08 | 1958-05-06 | Jerome J Sloyan | Anti-friction support |
US3318170A (en) * | 1965-08-05 | 1967-05-09 | Bendix Corp | No-lash axially movable steering column |
NO772853L (no) * | 1976-08-23 | 1978-02-24 | Uni Drive Tractors Ltd | Mekanisk leddforbindelse. |
DE3131321A1 (de) * | 1981-08-07 | 1983-02-24 | Skf Kugellagerfabriken Gmbh | Waelzlageranordnung fuer laengsbewegungen eines gehaeuses auf einer oder auf zwei zueinander parallelen schienen |
DE3444134C2 (de) * | 1984-09-12 | 1986-10-09 | Gebr. Bode & Co GmbH, 3500 Kassel | Kugelschraubgetriebe zur Umwandlung einer axialen Bewegung in eine Drehbewegung und umgekehrt für Maschinenbauteile |
DE3539860A1 (de) * | 1985-11-09 | 1987-05-14 | Kugelfischer G Schaefer & Co | Kugelhuelse |
DE19952245C2 (de) * | 1998-12-05 | 2002-11-28 | Gkn Loebro Gmbh | Teleskopwelle |
DE10053987A1 (de) * | 2000-10-31 | 2002-05-08 | Ina Schaeffler Kg | Längenverstellbare Welle |
US6676118B2 (en) * | 2001-08-13 | 2004-01-13 | Cheng-Ming Chou | Adjustable casing for helical spring |
US7018299B2 (en) * | 2003-05-21 | 2006-03-28 | Torque-Traction Technologies, Inc. | Rolling ball spline slip joint with helically shaped cage |
-
2004
- 2004-10-29 US US10/562,429 patent/US20070021223A1/en not_active Abandoned
- 2004-10-29 DE DE112004001172T patent/DE112004001172D2/de not_active Ceased
- 2004-10-29 WO PCT/EP2004/012312 patent/WO2006048029A1/de active Application Filing
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1800996U (de) | 1959-05-12 | 1959-11-26 | Wolfgang Grauff | Kugelgeradfuehrung. |
FR1373752A (fr) * | 1963-08-12 | 1964-10-02 | Glaenzer Spicer Sa | Dispositif de coulissement pour transmission d'un couple, à corps de roulement et ressorts de localisation de ces derniers |
DE2532661A1 (de) * | 1975-07-22 | 1977-01-27 | Walterscheid Gmbh Jean | Teleskopwelle, insbesondere fuer landmaschinen |
EP0189011A2 (de) | 1985-01-22 | 1986-07-30 | Affärsverket FFV | Teleskopische Welle insbesondere zur Drehmomentübertragung |
DE3940488A1 (de) * | 1989-12-07 | 1991-06-13 | Schaeffler Waelzlager Kg | Kugellaengsfuehrung, insbesondere fuer teleskopantriebswellen |
DE19609423A1 (de) | 1996-03-11 | 1997-09-18 | Loehr & Bromkamp Gmbh | Gelenkwelle, insbesondere Seitenwelle zum Antrieb der Räder eines Kraftfahrzeuges |
US6343993B1 (en) | 1999-06-30 | 2002-02-05 | Nacam France S.A. | Ball-type system for coupling two sliding shafts |
DE10233758A1 (de) | 2002-07-25 | 2004-03-11 | GKN Löbro GmbH | Längsverschiebeeinheit mit Bremsrollen |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1956252A1 (de) | 2007-02-09 | 2008-08-13 | Spicer Gelenkwellenbau GmbH | Längsverschiebeeinheit für Gelenkwellen |
CN107208690A (zh) * | 2015-02-16 | 2017-09-26 | 罗伯特博世汽车转向有限公司 | 用于机动车的转向中间轴以及用于运行用于机动车的转向中间轴的方法 |
WO2019220053A1 (fr) * | 2018-05-15 | 2019-11-21 | Safran Aircraft Engines | Dispositif de transmission de couple a frottements reduits |
FR3081197A1 (fr) * | 2018-05-15 | 2019-11-22 | Safran Aircraft Engines | Dispositif de transmission de couple a frottements reduits |
US11378014B2 (en) | 2018-05-15 | 2022-07-05 | Safran Aircraft Engines | Torque transmission device with reduced friction |
Also Published As
Publication number | Publication date |
---|---|
DE112004001172D2 (de) | 2006-08-24 |
US20070021223A1 (en) | 2007-01-25 |
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