GB2206175A - Variable phase rotary drive arrangements - Google Patents

Variable phase rotary drive arrangements Download PDF

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Publication number
GB2206175A
GB2206175A GB08815066A GB8815066A GB2206175A GB 2206175 A GB2206175 A GB 2206175A GB 08815066 A GB08815066 A GB 08815066A GB 8815066 A GB8815066 A GB 8815066A GB 2206175 A GB2206175 A GB 2206175A
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United Kingdom
Prior art keywords
rotation
drive arrangement
arrangement according
driven
camshaft
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Withdrawn
Application number
GB08815066A
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GB8815066D0 (en
Inventor
Frederick Michael Stidworthy
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Individual
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Individual
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Publication date
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Publication of GB8815066D0 publication Critical patent/GB8815066D0/en
Publication of GB2206175A publication Critical patent/GB2206175A/en
Withdrawn legal-status Critical Current

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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
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/02—Gearings or mechanisms with other special functional features for conveying rotary motion with cyclically varying velocity ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/348—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear by means acting on timing belts or chains
    • 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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • 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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0863—Finally actuated members, e.g. constructional details thereof
    • F16H2007/0874—Two or more finally actuated members

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

A rotary drive arrangement comprises a crankshaft (1) provided with a pulley or sprocket wheel (2), a camshaft (3) provided with a pulley or sprocket wheel (4) and an endless flexible drive element (5) in the form of a belt or chain engaged around the pulleys or sprocket wheels, so that rotation of crankshaft (1) causes rotation of camshaft (3). Guide means (8) for engaging and displacing the drive element (5) in order to vary the phase of the rotation of the camshaft relative to the rotation of the crankshaft comprises a slidable carrier bar (9) carrying freely running guide pulleys or sprocket wheels (10, 11) engaging the forward (6) and return (7) runs of the drive element (5). The carrier 9 is displaceable between extreme left and right hand positions to vary the phase of rotation of the camshaft through a predetermined range. <IMAGE>

Description

Description of Invention "Variable phase rotary drive arrangements" THIS INVENTION relates to variable phase drive arrangements in which a driving rotatable member drives a driven rotatable member such that the phase of the rotation of the driven member may be varied with respect to the rotation of the driving member.
The invention finds particular application in providing variation in the phase of the rotation of a camshaft relative to the rotation of a driving shaft, such as the crankshaft of an internal combustion engine, thereby enabling the timing of valves actuated by the cams on the camshaft to be varied in a controlled fashion.
According to the present invention, a variable phase rotary drive arrangement comprises a driving rotatable member, a driven rotatable member, an endless flexible drive element extending around and coupled to both the driving member and the driven member, so that rotation of the driving member causes rotation of the driven member, first guide means engaging and guiding the drive element during its movement along a first run towards the driven member, second guide means engaging and guiding the drive element during its movement along a second run away from the driven member, and means for simultaneously displacing the first and second guide means to vary the lengths of the respective guided runs of the drive element by equal amounts and in opposite senses in order to vary the phase of the rotation of the driven member with respect to the rotation of the driving member.
Embodiments of the present invention offer a simple way of varying the characteristics of an internal combustion engine having a camshaft driven from a crankshaft by means of a timing belt or chain. By changing the phase relationship between the crankshaft and camshaft rotations, the operation of the engine valves can be adjusted depending upon the running conditions in order to achieve fuel savings, cleaner engine emissions, and improvements in torque.
In order that the invention may be readily understood, embodiments thereof will now be described, by way of example, with reference to the accompanying drawings, in which: Figures 1A and 1B are diagrammatic end views of a first rotary drive arrangement embodying the invention, showing linearly displaceable guide means of the arrangement in two extreme positions; Figures 2A, 2B, 2C are diagrammatic end views of a second rotary drive arrangement embodying the present invention, angularly displaceable guide means of the arrangement being shown in respective extreme positions in Figures 2A and 2C and in an intermediate position in Figure 2B;; Figures 3A and 3B are diagrammatic end views of a third rotary drive arrangement embodying the present invention, angularly displaceable guide means of the arrangement being shown in respective extreme positions in the two Figures; Figure 4 is a side view of a fourth rotary drive arrangement embodying the present invention, in which two coaxial camshafts are separately driven by a common crankshaft;; Figures 5A, 5B and 5C are diagrammatic end views of a fifth rotary drive arrangement embodying the present invention, in which two parallel camshafts are driven through a common drive element by a common crankshaft, Figures 5A and 5C showing linearly displaceable guide means of the arrangement in respective extreme positions and Figure 5B showing the guide means in an intermediate position; Figures 6A and 6B are diagrammatic end views of a sixth rotary drive arrangement embodying the present invention and show angularly displaceable guide means of the arrangement in respective extreme positions;; Figure 7 is an end view illustrating a seventh rotary drive arrangement embodying the present invention, in which the timing of the rotation of two camshafts driven by a common camshaft is variable by means of linearly displaceable guide means relative to the rotation of the crankshaft; Figure 8 is a diagrammatic end view of an eight rotary drive arrangement embodying the present invention in which two camshafts are driven by a common camshaft and the rotation of one of the camshafts is varied by means of an angularly displaceable guide means; Figure 9 is a diagrammatic end view of a ninth rotary drive arrangement embodying the present invention, in which the timing of two camshafts is variable by means of linearly displaceable guide means relative to the rotation of a common camshaft by which they are driven; and Figures 10A and 10B are diagrammatic end views showing a tenth embodiment of the present invention with linearly displaceable guide means in respective extreme positions.
Throughout the Figures of the drawings, like components in the various embodiments are indicated by like reference numerals.
Referring firstly to Figures 1A and 1B, a rotary member in the form of a crankshaft 1 is provided with a coupling element in the form of a pulley or sprocket wheel 2 and serves to drive a driven rotary member in the form of a camshaft 3 which is rotatable about an axis parallel to the axis of rotation of the camshaft and which is provided with a coupling element in the form of pulley or sprocket wheel 4. A flexible drive element in the form of an endless belt or chain 5 extends closely around the coupling elements 2 and 4 to engage the coupling elements and rotate the camshaft 3 upon rotation of the crankshaft 1.In the following description it is assumed that the crankshaft 1 rotates in an anticlockwise direction to cause the camshaft 3 to rotate similarly in an anti-clockwise direction, although of course the crankshaft could be driven in the clockwise direction to rotate the camshaft in the clockwise direction The drive element 5 has a first run 6 towards the driven member and a second run 7 away from the driven member.
The rotary drive arrangement of Figures 1A and 1B comprises linearly displaceable guide means 8 for engaging and displacing the drive element 5 so as to vary the lengths of the runs 6 and 7 by equal amounts in opposite directions in order to vary the timing of the rotation of the camshaft 3 relative to the rotation of the crankshaft 1. The guide means 8 comprise a carrier in the form of a bar 9 guided for sliding movement over a limited range transversely of the parallel axis of rotation of the camshaft 3 and crankshaft 1 and carrying first and second guide elements 10 and 11 for respectively engaging the first and second runs 6 and 7 of the drive element 5.The guide elements 10 and 11 take the form of idler pulleys or sprocket wheels mounted on idler axles 13 and 14 on the bar 9 so as to be freely rotatable about axes parallel to the axes of rotation of the shafts 1 and 3, the carrier bar being of a length such that, within its range of sliding movement, r the guide elements 10 and 11 remain engaged with the respective runs 6 and 7 of the drive element 5.
Figures 1A and 1B show the carrier bar 9 in respective extreme right hand and left hand positions, from which it can be seen, referring to the indicator 12 marked on the coupling element 4, that the phase of camshaft rotation can be varied relative to the crankshaft rotation through a range of about 240 by movement of the slide bar between these extreme positions. That is, there is a range of adjustment extending 120 on either side of a mean position defined by a mean position of the carrier bar 9 mid-way between the illustrated extreme positions. The slide bar 9 is arranged to be moved by suitable adjusting means (no5 shown) into any selected position between the illustrated extreme positions and held in the selected position, so that the timing of the camshaft rotation relative to the camshaft rotation is effectively steplessly variable and selectable within the indicated range of 240. The adjusting means may be controlled in accordance with the operating conditions of the engine or in accordance with some other selected parameter or parameters to optimise one or more operating characteristic of an engine in which the camshaft 3 is incorporated.
The second embodiment of the invention shown in Figures 2A, 2B and 2C differs from the first embodiment in that the guide elements 10 and 11 are carried on respective arms 15 and 16 extending from a hub 17 mounted on the camshaft nose for rotation about the same axis as the camshaft 3. The guide elements are mounted for free rotation on the extremeties of the arms 13 and 14 by idler 13 and 14 axles. In this embodiment, the forward and return runs 6 and 7 of the drive element 5 pass through the gap between the guide elements 10 and 11, so as to be pinched towards one another in the intermediate or mean position of the guide means shown in Figure 2B.
The hub 17 is angularly displaceable by suitable adjusting means (not shown) between the extreme positions shown in Figures 2A and 2C which are angularly spaced apart such that the guide elements 10 and 11 retain in contact with the respective runs 6 and 7 of the drive element 5. The range of angular adjustment of the hub 15 is 56.500, which results in the phase of the rotation of the camshaft being adjustable through a total angle of 490 relative to the rotation of the crankshaft 1. The hub 17 can be held in any selected position within this adjustment range by the adjusting means.
Figures 3A and 3B illustrate a third embodiment of the invention which is similar to the second embodiments except that the guide elements 10 and 11 are mounted on arms 15 and 16 at the end of an extension arm 18 carried by a hub 19 mounted for limited angular displacement about the same axis as the crankshaft 1.The hub 19 is rotatable through an angle of 29 between the two extreme positions shown in Figures 3A and 3B to provide adjustment of the rotational phase of the camshaft 3 relative to the crankshaft rotation through a range of 430 Figure 4 shows a drive arrangement in which a single crankshaft 1 drives concentric camshafts 3a and 3b by means of respective endless drive elements 5a and 5b engaged around respective coupling elements 2a, 4a and 2b, 4b on the crankshaft and the camshafts. Outer camshaft 3b comprises first and second sleeve shafts 20 and 21 rotatably received on inner camshaft 3a.Sleeve shaft 20 has a cam 22 engaged with a cam 23 on the sleeve shaft 21 via a lever 24 pivotally mounted on a stub axle 25 which is fixed to or part of camshaft 3a and which has an end cap 26 retaining the lever 24 on the stub axle 25.
The relative rotational timing of the cams 22 and 23 can be varied by causing sleeve shaft 20 to rotate on inner camshaft 3a, the lever action exerted by lever 24 between cams 22 and 23 causing the cam 23 to rotate in the opposite direction to cam 22. Accordingly, if the drive element 5b is provided with guide means of the kind described in the previous embodiments, then the rotational phase of sleeve shaft 20 can be varied relative to that of the crankshaft 1 and the inner camshaft 3a in order to change the relative rotation phases of the cams 22 and 23. The rotational phase of further cam 27 on sleeve shaft 21 is, of course, varied with the phase of cam 23.
The arrangement depicted in Figure 4 offers phase changing capability on a single composite camshaft provided with both inlet and exhaust cams. For example, cam 22 could be an inlet cam and cam 23 an outlet cam which need to be adjusted in place in opposite directions.
A similar phase changing device could be included in the drive from the crankshaft 1 to the inner camshaft 3a, if desired.
Referring now to Figures 5A to 5C, a fifth rotary drive arrangement embodying the present invention comprises a pair of camshafts 3c and 3d which are rotatable about respective parallel axes and are driven by a single crankshaft 1 to which camshafts are coupled by means of a single drive element 5 engaging respective coupling elements 2, 4c and 4d on the crankshaft and camshafts. Guide means in the form of guide elements 10 and 11 engage respective forward and return runs 6 and 7 to and from the camshaft 3a, the guide elements 10 and 11 pinching the runs 6 and 7 there-between and being coupled together by adjusting means (hot shown) for limited displacement along respective linear paths in directions 30 and 31 such that both of the guide elements 10, 11 remain in engagement with the drive element 5 over the range of movement provided.Figure 5B shows a mean position of the guide elements. Displacement of the guide element 10 inwardly to the position 10a shown in phantom in Figure 5B together with simultaneous movement of the guide element 11 outwardly to the position 11a shown in phantom brings the arrangement into one extreme position which is shown in Figure 5A, thereby retarding the phase of the rotation of camshaft 3C by 41 relative to the position shown in Figure 5B.Similarly, displacing the guide element 10 outwardly from the Figure 5A position with simultaneous inward movement of the guide element 11 leads to the other extreme position shown in Figure 5B and advances the phase of rotation of the camshaft 3a relative to the rotation of the crankshaft 1 by 410 relative to the position shown in Figure 5B. An overall range of adjustment of 820 in the phase rotation of the camshaft 3C is thereby provided and any position within this range can be selected and held by the adjusting means.
The sixth embodiment of the invention shown in Figures 6A and 6B is similar to the fifth embodiment, except that the guide elements 10 and 11 are mounted on an angularly displaceable hub 17c supported for rotation about the same axis as the camshaft 3c, the hub being pivotable by adjusting means through an angle of 600 between the two extreme positions shown in Figures 6A and 6B in order to provide a range of 720 of suitable adjustment in the phase of rotation of the camshaft 3c relative to the crankshaft 1. The guide elements 10 and 11 are mounted freely rotatably on axles 13c. and 14c on respective arms 15c, 16c extending from the hub.The hub 17c carries a partial worm-wheel 40 which is engaged with a worm 41 which serves as the adjustmetn means to adjust the angular position of the hub 17c and then to lock the hub in the adjusted position. The worm wheel 40 and worm 41 engage at a locking angle of about 10 to preclude rotation of the worm by the worm-wheel and thereby hold the hub 17c in its adjusted position.
Figure 7 shows an embodiment of the invention, in which the guide means comprises three linearly displaceable guide elements 10, 11 and 50 mounted freely rotatable on respective axles 13, 14 and 51 carried by adjusting means for linearly displacing the guide elements along respective directions 52, 53 and 54. The guide elements 10, 11 and 50 act on respective runs 6, 7 and 55 of the drive element 5 and are displaceable in concert by the adjusting means to positions 10a, lia and 50a to vary the phase of rotation of both of the camshafts 3c and 3d simultaneously relative to the crankshaft 1 over respective ranges of 170. In this displacement, the guide element 11 moves a distance equal to the sum of the distances moved by the two guide elements 10 and 50. If one or other only of the guide elements 10 and 50 is displaced and guide element 11 is simultaneously displaced by an equal amount, then only the respective camshaft 3c or 2d will undergo a change of phase.
Figure 8 shows an embodiment of the invention which is similar to the embodiment of Figures 6a and 6b, but where the guide elements 10 and 11 are carried on a hub 17d mounted for rotation about the same axis as camshaft 3d and where the arms 15d and 16d on which the guide elements are mounted by axles 13d and 14d are of different length. Angular displacement of the hub 17d through an angle of 5110 by suitable adjusting means, such as a worm and worm-wheel provides a range of 720 of phase rotation in the rotation of camshaft 3d.
The embodiment of Figure 9 is similar to that of Figure 7, except that the guide elements 10 and 50 are disposed within the endless drive element 5, the guide element 11 still being located outside the drive elements. This arrangement provides phase variation of the rotation of the two camshafts over equal ranges of 130 upon displacement of the guide elements to the positions 10b, lib and 50b.
Figures 10A and 10B illustrate an embodiment of the invention which is similar to the embodiment of Figure 7 for the case where two camshafts 3c and 3d are located in close proximity to one another. The total phase adjustment offered by this layout is 690 between the two extreme positions shown respectively in Figures 10A and lOB.

Claims (15)

CLAIMS:
1. A drive arrangement comprising a driving rotatable member, a driven rotatable member, an endless flexible drive element extending around and coupled to both the driving member and the driven member so that rotation of the driving member causes rotation of the driven member, first guide means engaging and guiding the drive element during its movement along a first run towards the driven member, second guide means engaging and guiding the drive element during its movement along a second run away from the driven member, and means for simultaneously displacing the first and second guide means to vary the lengths of their respective guided runs by equal amounts and in opposite senses in order to vary the phase of the rotation of the driven member with respect to the rotation of the driving member.
2. A drive arrangement according to claim 1, wherein the first and second guide means are coupled together for movement along respective linear paths.
3. A drive arrangement according to claim 2, wherein the first and second guide means move along co-linear paths.
4. A drive arrangement according to claim 2, wherein the first and second guide means are coupled together for arcuate movement about a common axis.
5. A drive arrangement according to claim 4, wherein the common axis is the axis of rotation of the driven member.
6. A drive arrangement according to claim 4, wherein the common axis is the axis of rotation of the driving member.
7. A drive arrangement according to claim 11, 5 or 6, wherein the guide means are mounted on a common hub which is angularly adjustable about the common axis of rotation by adjusting means serving to rotate the hub into an adjusted position and to hold the hub in the adjusted position.
8. A drive arrangement according to claim 7, wherein the adjusting means comprises a worm engaging at least a segment of a worm-wheel fixed to the hub, the worm and worm-wheel engaging one another at a locking angle precluding rotation of the worm by the worm-wheel.
9. A drive arrangement according to any preceding claim, wherein two driven members are driven by the same driving member via respective flexible drive elements.
10. A drive arrangement according to any one of claims 1 to 8, wherein two driven members are driven by the same driving member via a single flexible drive element.
11. A drive arrangement according to any preceding claim, wherein the driving member is a crankshaft and the or each driven member is a camshaft.
12. A drive arrangement according to any preceding claim, wherein the driving member and the or each driven member each carry with a coupling element in the form of a pulley and the or each drive element is an endless drive belt.
13. A drive arrangement according to any one of claims 1 to 11, wherein the driving member and the or each driven member each carry coupling in the form of a sprocket wheel and the or each drive element is an endless chain.
14. A rotary drive arrangement substantially as hereinbefore described with reference to the accompanying drawings.
15. Any novel feature or combination of features described herein.
GB08815066A 1987-06-25 1988-06-24 Variable phase rotary drive arrangements Withdrawn GB2206175A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB878712945A GB8712945D0 (en) 1987-06-25 1987-06-25 Variable valves

Publications (2)

Publication Number Publication Date
GB8815066D0 GB8815066D0 (en) 1988-08-03
GB2206175A true GB2206175A (en) 1988-12-29

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GB878712945A Pending GB8712945D0 (en) 1987-06-25 1987-06-25 Variable valves
GB08815066A Withdrawn GB2206175A (en) 1987-06-25 1988-06-24 Variable phase rotary drive arrangements

Family Applications Before (1)

Application Number Title Priority Date Filing Date
GB878712945A Pending GB8712945D0 (en) 1987-06-25 1987-06-25 Variable valves

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Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2218736A (en) * 1988-05-10 1989-11-22 Borg Warner Automotive Variable relative timing system for shafts connected by an endless member
GB2232456A (en) * 1989-06-08 1990-12-12 Heidelberger Druckmasch Ag Drive wheel phase relationship adjustment device
GB2238348A (en) * 1989-11-15 1991-05-29 * Rover Group Limited Endless loop i.c. engine valve timing varying mechanism
GB2244783A (en) * 1990-06-07 1991-12-11 Ford Motor Co Phase changing mechanism
GB2245047A (en) * 1990-06-12 1991-12-18 Ford Motor Co Phase change mechanism
WO1993006386A1 (en) * 1991-09-25 1993-04-01 Summagraphics N.V. Sprocket control apparatus
WO1995009993A1 (en) * 1993-10-01 1995-04-13 Marantec Antriebs- Und Steuerungstechnik Gmbh & Co. Produktions Kg System for a friction gear
EP0687834A1 (en) * 1994-06-16 1995-12-20 CTA International Transmission device with a controlled tensioner
EP0719962A2 (en) * 1994-12-30 1996-07-03 KOENIG &amp; BAUER-ALBERT AKTIENGESELLSCHAFT Tensioning device for a toothed belt
DE19624311C1 (en) * 1996-06-18 1998-04-02 Ingo Mussehl Rear chain drive for off road motorcycle
FR2763096A1 (en) * 1997-05-09 1998-11-13 Vianney Paul Rabhi IC engine with variable cylinder capacity or volume ratio
WO1998051911A1 (en) * 1997-05-09 1998-11-19 Vianney Rabhi Device for varying a piston engine effective volumetric displacement and/or volumetric ratio of during its operation
DE10000970A1 (en) * 2000-01-12 2001-09-06 Litens Automotive Gmbh Clamping device for a flexible drive element
NL1019063C2 (en) * 2001-03-21 2002-09-24 Hesling B V Chain tensioner for bicycle is on end of spring-loaded arm which pivots on crankshaft
FR2868494A1 (en) * 2004-04-05 2005-10-07 Roger Lecal Rotary transmission`s angular phase shifter for internal combustion engine, has rollers on driving/driven strand at interior/exterior and at middle of belt, and obtaining involutes with correction angle higher than course of control
GB2437151A (en) * 2006-04-07 2007-10-17 Paul Brian Chatten Mechanism for varying the relative phase angle of pulleys or sprockets connected by a chain or toothed belt
FR2979946A3 (en) * 2011-09-13 2013-03-15 Renault Sa Rotational offset system for camshaft connected to crankshaft of two-stroke internal combustion engine of motor vehicle, has displacement unit for displacing branches of belt according to transverse axis parallel and orthogonal to planes
EP2826964A1 (en) * 2013-07-15 2015-01-21 MWM GmbH Variable actuation timing device
US20220235851A1 (en) * 2021-01-22 2022-07-28 Borgwarner Inc. Method(s) to apply tension to increase drivetrain jump torque capacity
US12078245B2 (en) 2022-05-31 2024-09-03 Borgwarner Inc. Face of tensioner guide or arm with pattern to influence chain system NVH performance

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GB587088A (en) * 1944-01-03 1947-04-14 Standard Telephones Cables Ltd Improvements in mechanisms for adjusting the relative angular position of interconnected shafts
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GB918162A (en) * 1961-08-22 1963-02-13 Macalisters Ltd Device for use in conjunction with conveyor belts and the like
GB1223329A (en) * 1967-12-26 1971-02-24 Byron Jackson Inc Combined power tong and back-up tong assembly
GB1513722A (en) * 1974-06-26 1978-06-07 Renold Ltd Damper apparatus for applying a tensioning force to a member
GB1585624A (en) * 1977-08-19 1981-03-11 Cancilla P Chain tensioner for chain drives
US4685429A (en) * 1985-05-14 1987-08-11 Yamaha Valve timing control means for engine

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Publication number Priority date Publication date Assignee Title
GB587088A (en) * 1944-01-03 1947-04-14 Standard Telephones Cables Ltd Improvements in mechanisms for adjusting the relative angular position of interconnected shafts
GB861741A (en) * 1958-08-12 1961-02-22 Perry Chain Company Ltd Improvements relating to chain and belt-tensioning means
GB918162A (en) * 1961-08-22 1963-02-13 Macalisters Ltd Device for use in conjunction with conveyor belts and the like
GB1223329A (en) * 1967-12-26 1971-02-24 Byron Jackson Inc Combined power tong and back-up tong assembly
GB1513722A (en) * 1974-06-26 1978-06-07 Renold Ltd Damper apparatus for applying a tensioning force to a member
GB1585624A (en) * 1977-08-19 1981-03-11 Cancilla P Chain tensioner for chain drives
US4685429A (en) * 1985-05-14 1987-08-11 Yamaha Valve timing control means for engine
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Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2218736A (en) * 1988-05-10 1989-11-22 Borg Warner Automotive Variable relative timing system for shafts connected by an endless member
GB2218736B (en) * 1988-05-10 1992-12-16 Borg Warner Automotive An internal combustion engine with a variable camshaft timing system.
GB2232456A (en) * 1989-06-08 1990-12-12 Heidelberger Druckmasch Ag Drive wheel phase relationship adjustment device
GB2232456B (en) * 1989-06-08 1993-06-16 Heidelberger Druckmasch Ag Drive wheel phase relationship adjustment device
GB2238348B (en) * 1989-11-15 1993-09-22 Rover Group A mechanism to vary the valve timing in an internal combustion engine
GB2238348A (en) * 1989-11-15 1991-05-29 * Rover Group Limited Endless loop i.c. engine valve timing varying mechanism
GB2244783A (en) * 1990-06-07 1991-12-11 Ford Motor Co Phase changing mechanism
GB2244783B (en) * 1990-06-07 1994-01-12 Ford Motor Co Phase changing mechanism
GB2245047A (en) * 1990-06-12 1991-12-18 Ford Motor Co Phase change mechanism
GB2245047B (en) * 1990-06-12 1994-01-12 Ford Motor Co Phase change mechanism
WO1993006386A1 (en) * 1991-09-25 1993-04-01 Summagraphics N.V. Sprocket control apparatus
US5316523A (en) * 1991-09-25 1994-05-31 Summagraphics N.V. Sprocket control apparatus
WO1995009993A1 (en) * 1993-10-01 1995-04-13 Marantec Antriebs- Und Steuerungstechnik Gmbh & Co. Produktions Kg System for a friction gear
EP0687834A1 (en) * 1994-06-16 1995-12-20 CTA International Transmission device with a controlled tensioner
FR2721366A1 (en) * 1994-06-16 1995-12-22 Giat Ind Sa Belt transmission with drive and driven wheels incorporating pilot operated tensioning
US5750916A (en) * 1994-06-16 1998-05-12 Cta International Transmission device having a central rotating wheel and a laying mechanism with such a device
EP0719962A3 (en) * 1994-12-30 1997-09-10 Koenig & Bauer Albert Ag Tensioning device for a toothed belt
EP0719962A2 (en) * 1994-12-30 1996-07-03 KOENIG &amp; BAUER-ALBERT AKTIENGESELLSCHAFT Tensioning device for a toothed belt
DE19624311C1 (en) * 1996-06-18 1998-04-02 Ingo Mussehl Rear chain drive for off road motorcycle
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GB2437151A (en) * 2006-04-07 2007-10-17 Paul Brian Chatten Mechanism for varying the relative phase angle of pulleys or sprockets connected by a chain or toothed belt
GB2437151B (en) * 2006-04-07 2011-04-06 Paul Brian Chatten Mechanism for varying the phase angle of pulleys or sprockets when connected by a continuous toothed belt or chain to provide discreet valve timing
FR2979946A3 (en) * 2011-09-13 2013-03-15 Renault Sa Rotational offset system for camshaft connected to crankshaft of two-stroke internal combustion engine of motor vehicle, has displacement unit for displacing branches of belt according to transverse axis parallel and orthogonal to planes
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US20220235851A1 (en) * 2021-01-22 2022-07-28 Borgwarner Inc. Method(s) to apply tension to increase drivetrain jump torque capacity
US11796040B2 (en) * 2021-01-22 2023-10-24 Borgwarner Inc. Method(s) to apply tension to increase drivetrain jump torque capacity
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GB8815066D0 (en) 1988-08-03
GB8712945D0 (en) 1987-07-08

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