(12) UK Patent Application (19) GB (11) 2 296 481 (13) A
`
`(43) Date of A Publication 03.07.1996
`
`(51)
`
`INTCL6
`B66D 1/39
`
`(52) UK CL !Edition 0 )
`88B BCDD
`
`(56) Documents Cited
`GB 2271973 A GB 2183212 A
`EP 0043367 A2.
`GB 0714071 A
`
`GB 2158032 A
`US4972778 A
`
`(58) Field of Search
`UK CL !Edition N ) 888 BCDD
`INTCL6 B66D1/39
`
`(211 Application No 9423979.5
`
`(22) Date of Filing 28.11.1994
`
`(711 Applicant(s)
`Stage Technologies Ltd
`
`(Incorporated in the United Kingdom)
`
`3A Aberdeen Studios, 22 Highbury Grove, LONDON,
`NS 2DQ, United Kingdom
`
`(72)
`
`lnventor(s)
`Michael Barnet
`
`(741 Agent and/or Address for Service
`Boult Wade Tennant
`27 Furnival Street, LONDON, EC4A 1 PO.
`United Kingdom
`
`(54) ZERO FLEET ANGLE WINCH
`
`(57) A winch comprises a frame 12 a carriage 36 adapted for movement with respect to the frame and a
`cylindrical drum 14 mounted on the carriage for rotation with respect to the carriage about an axis extending
`generally axially of the drum. A cable 16 is attached to the drum 14 and adapted to be wound around a
`circumferential surface thereof. Drive means 18 is mounted on the carriage for rotating the drum about the
`axis and means are provided for moving the carriage with respect to the frame in a linear direction axially of
`the drum such that upon each rotation of the drum the drum moves axially relative to the frame by a distance
`equal to that separating adjacent turns of the cable when measured parallel to the drum axis. As shown the
`latter means comprises a rotatable threaded rod 58 engaging a threaded bore 34 on the frame. Alternatively
`the threaded rod may be fixed and a rotatable nut mounted on the carriage.
`
`/7t9/
`
`At least one drawing originally filed was informal and the print reproduced here is taken from a later filed formal copy.
`
`This print takes account of replacement documents submitted after the date of filing to enable the application to comply
`with the formal requirements of the Patents Rules 1995
`1 of 15
`
`Daktronics, Inc.
`STAGE EXHIBIT 1005
`EXHIBIT 1005
`
`

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`

`
`2296481
`
`-
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`1 -
`
`ZERO FLEET ANGLE WINCH
`
`The present invention relates to winches and in
`particular, but not exclusively, to winches for use in
`theatres for moving various items of scenery.
`In the past winches have comprised a cylindrical
`drum which is rotatably driven about a substantially
`horizontial shaft which extends axially of the drum.
`A cable is wound around a circumferential surf ace of
`the drum to which it is attached at one end.
`Typically the cable passes over a pulley and the
`opposite end of the cable is attached to an item to be
`moved by the winch so that, for example, as the cable
`is wound onto the drum the item to be moved is drawn
`in the direction of the winch.
`In order to guide the cable on to the drum and
`prevent the cable from slipping with respect to the
`circumferential surf ace in a direction parallel to the
`drum axis, the circumferential surface of the drum is
`often provided with a helical groove of sufficient
`dimensions to accommodate the cable. Even so, the
`fleet angle, that is the angle subtended between the
`cable and a plane perpendicular to the axis of the
`drum, must be smaller than three degrees to prevent
`the cable from riding up out of the helical groove and
`slipping axially of the drum. For a typical winch
`where the drum has a diameter of O.Jm this has
`necessitated placing the pulley at least 2m from the
`drum. This distance between the drum and the pulley
`represents dead or unusable space which, for example,
`in a theatre setting where space is restricted,
`represents a considerable problem.
`If the drum were
`to be replaced with one having a smaller diameter then
`the pulley would need to be placed even further away
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`2 -
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`while if the diameter of the drum were to be increased
`there would need to be a corresponding increase in the
`size of the motor and gear box through which the drum
`is rotatably driven. Thus in the past it has been
`accepted that a winch must of necessity be of a
`certain size that cannot be significantly reduced.
`In a theatre setting any winch is typically
`accommodated beneath the stage. Quite clearly
`however, the size of the winch has a significant
`impact on the cost of installation and its
`applicability for the performance of certain tasks.
`In order to reduce the amount of dead space
`between the pulley and the drum, a number of attempts
`have been made to devise a winch which maintains a
`zero fleet angle. One such attempt has involved
`moving the drum in an axial direction as it rotates so
`that for each revolution the drum moves axially by a
`distance equal to the pitch of the helical groove.
`However, such an arrangement requires the shaft about
`which the drum is rotated to slide with respect to the
`gearbox in order that it may accommodate the axial
`movement of the drum. Unfortunately this has led to
`problems with wear which have rendered the resulting
`winch impracticable.
`In another attempt to produce a zero fleet angle
`winch, the pulley has been positioned at the takeoff
`point at which the cable leaves the drum. The pulley
`has then been moved axially so that for each
`revolution of the drum the pulley moves by a distance
`equal to the pitch of the helical groove. This
`arrangement however suffers from the fact that the
`pulley is exposed to increased loads of typically up
`to half a ton.
`The present invention is directed at least in
`part to overcoming some of the problems associated
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`3 -
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`with the prior art.
`According to the present invention there is
`provided a winch comprising a frame, a carriage
`adapted for movement with respect to the frame, a
`cylindrical drum mounted on the carriage for rotation
`with respect to the carriage about an axis extending
`generally axially of the drum, a cable attached to the
`drum and adapted to be wound around a circumferential
`surface thereof, drive means mounted on the carriage
`for rotating the drum about said axis, and means for
`moving said carriage with respect to the frame in a
`linear direction axially of the drum such that upon
`each rotation of the drum said drum moves axially
`relative to the frame by a distance equal to that
`separating adjacent turns of the cable when measured
`parallel to the drum axis.
`In this way it will be apparent to those skilled
`in the art that the present invention provides a zero
`fleet angle winch which is neither exposed to
`excessive wear or transmits an increased load to the
`pulley. Furthermore, by providing a satisfactory zero
`fleet angle winch, it has become possible to reduce
`the diameter of the drum without increasing the
`associated dead space between the drum and the pulley.
`Having reduced the diameter of the drum it has then
`been possible to reduce the size of the gearbox and
`drive means for rotating the drum which in turn has
`led to an overall reduction in the size of the winch.
`This size reduction enables savings in both
`manufacturing costs and the cost of installation.
`Finally, by providing a winch which is reduced in
`size, it is possible for the winch to find use in
`applications where heretofor such use would not have
`been possible such as, for example, in situations
`where the available space is severely limited.
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`An embodiment of the present invention will now
`be described by way of example with reference to the
`accompanying drawings in which:
`Figure 1 is a cross sectional view of a prefered
`embodiment of the present invention; and
`Figure 2 is an end view of the embodiment of
`Figure 1.
`Referring to Figures 1 and 2, there is shown a
`winch 10 comprising a frame 12, a cylindrical drum 14
`mounted to the frame, a cable 16 attached to the drum
`and drive means 18 for rotating the drum with respect
`to the frame.
`Looking in more detail at Figure 2, the frame 12
`can be seen to comprise two longitudinally extending
`side walls 20, 22 which are held in spaced
`relationship by means of a pair of cross braces 24, 26
`welded to their under surfaces. The two side walls
`20, 22 are both of substantially c-shaped cross
`section and so define respective longitudinal channels
`28 and 30 which open inwardly of the side walls. An
`upstanding projection 32 is provided on a first of the
`cross braces 24 centrally of the side walls 20 and 22
`and defines a threaded through bore 34.
`In addition to the upstanding projection 32,
`there is also disposed between the two side walls 20
`and 22, a carriage 36. The carriage 36 comprises a
`supporting platform in the form of plate 38 having a
`lateral dimension which enables the plate when placed
`centrally between the side walls 20 and 22 to define
`respective slots 40 and 42 which extend longitudinally
`between the cross braces 24 and 26. The carriage 36
`is supported for longitudal movement with respect to
`the frame 12 by means of four flanged wheels 44 which
`are received within the channels 28 and 30. As can be
`seen from Figure 2, each wheel 44 is mounted in a set
`
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`of bearings 46 for rotation with respect to an axle
`assembly '48 which in turn depends from an undersurface
`of the supporting plate 38.
`In addition to the four axle assemblies 48, the
`supporting plate 38 is also provided on its
`undersurface with a depending projection 50 which is
`located centrally of the side walls 20 and 22 and
`rearwardly of the upstanding projection 32. Like the
`upstanding projection 32, the depending projection 50
`defines a through bore 52 which is in axial alignment
`with the threaded through bore 34.
`At a forward end of the carriage 36, the
`supporting plate 38 is provided with a front wall 54
`which both extends upwardly from the plate and
`downwardly in the direction of the cross brace 26.
`This downwardly extending portion is provided with a
`further through bore 56 in axial alignment with that
`provided in the depending projection 50 and the
`threaded through bore 34 provided in the upstanding
`projection 32. A longitudingly extending ACME screw
`threaded member 58 is received within the threaded
`through bore 34 and is supported between the depending
`projection 50 and the front wall 54. The ACME screw
`threaded member 58 is provided at opposite ends with a
`respective one of a pair of axially extending smooth
`stub portions 60, 62 which are of reduced diameter and
`which are received within the through bores 52 and 56.
`Respective bearings 64 and 66 are provided in
`association wi~h each of the through bores 52 and 56
`and facilitate the rotation of the ACME screw threaded
`member 58 with respect to the carriage 36.
`The upwardly extending portion of the front wall
`54 is also provided with a through bore 68 which
`receives the stub like end projection 70 of a
`longitudinally extending shaft 72. At an opposite
`
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`end, the shaft 72 is received within an axially
`aligned through bore 74 provided in a rear wall 76
`which, like the front wall 54, extends upwardly from
`the supporting plate 38.
`Intermediate the front and
`rear walls 54 and 76, the supporting plate 38 is
`provided with its own upstanding projection 78 and
`this also defines a through bore 80 in axial alignment
`with that provided in the upwardly extending portion
`of the front wall. All three through bores 68, 74 and
`78 are each associated with a respective set of
`bearings 82, 84 and 86 to facilitate the rotation of
`the shaft 72 with respect to the carriage 36.
`As can be seen from Figure 1, the cylindrical
`drum 14 is arranged co-axially of the shaft 72,
`intermediate the front wall 54 and the upstanding
`projection 78.
`In order to reduce the weight of the
`drum 14 and so minimise the power requirements of the
`drive means 18, the drum is formed as a hollow
`cylinder 88 and joined to the shaft 72 by means of a
`pair of axially spaced discs 90, 92 each having a
`central through bore 94 dimensioned to receive the
`shaft 72 and a diameter corresponding to the interior
`diameter of the cylinder 88. One end of the cable 16
`is secured to a first of the axially spaced disks 90
`by means of a threaded bolt 96 which is received
`within an appropriately threaded apperture 98. The
`cable 16 then passes exteriorly of the hollow cylinder
`88 through an appropriately dimensioned through bore
`100.
`
`The circumferential surface of the hollow
`cylinder 88 is provided with a helical groove 102
`which is dimensioned so as to be capable of receiving
`the cable 16. To this end the groove 102 preferably
`has a depth substantially equal to the radius of the
`cable and a width parallel to the drum axis slightly
`
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`7 -
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`greater than its diameter.
`The cylindrical drum 14 is rotatably driven with
`respect to the carriage 36 by means of a drive means
`18 in the form of an electric motor 104 and gear box
`106. The electric motor 104 is supported by the rear
`wall 76 and communicates with the shaft 72 by way of
`the gear box 106. The gear box 106 is located between
`the rear wall 76 and the upstanding projection 78 and
`is keyed to the shaft 72 by means of an appropriate
`keyway 108.
`At an end of the shaft 72 remote from the gear
`box 106, the stub like end projection 70 carries a
`flanged gear wheel 110 which is secured to, and
`rotates with, the stub like end projection by means of
`a grub screw 112. A second gear wheel 114 is secured
`to that part of the stub portion 62 of the ACME screw
`threaded member 58 which projects through the through
`bore 56 provided in the downwardly extending portion
`of the front wall 54. The two gear wheels 110 and 114
`are drivingly interconnected by means of a drive chain
`116.
`
`In use, when it is desired to wind the cable 16
`onto the cylindrical drum 14 the electric motor 104 is
`actuated by means of a suitable switch (not shown).
`The rotational movement generated within the electric
`motor 104 is transmitted to the shaft 72 by means of
`the gear box 106 and this in turn causes the rotation
`of the hollow cylinder 88. Depending on the direction
`of rotation, the cable 16 is then drawn onto the
`cylindrical drum 14 passing through the frame 12
`between the cross braces 24 and 26 and through the
`longitudinal slots 40 and 42.
`As well as causing the rotation of the
`cylindrical drum 14, the rotation of the shaft 72 also
`causes the rotation of the first of the two gear
`
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`- 8 -
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`wheels 110. This motion is in turn transmitted to the
`second gear wheel 114, and hence to the ACME screw
`threaded member 58, by way of the drive chain 116. As
`the ACME screw threaded member 58 rotates its
`engagement with the threaded through bore 34 of the
`outstanding projection 32 causes the entire carriage
`36 including the cylindrical drum 14, electric motor
`104 and gear box 106, to move longitudinally of the
`frame 12. This movement is facilitated by means of
`the rolling engagement of the four flanged wheels 44
`within the channels 28, 30 of the side walls 20, 22.
`Because of the gearing that exists between the first
`gear wheel 110 and the second gear wheel 114, each
`time the cylindrical drum 14 completes one rotation
`the carriage 36 moves longitudely by a distance equal
`to the pitch of the groove 102 provided in the
`circumferential surface of the drum 14.
`In this way
`the cable take off point remains fixed with respect to
`the frame 12 enabling the cable 16 to extend away from
`the cylindrical drum 14 in a plane which is always at
`right angles to the axis of rotation of the shaft 72.
`By ensuring that the cable 16 maintains a zero
`fleet angle, th~ described winch 10 is no longer
`subject to the dead space requirement associated with
`winches of the prior art. As a result it becomes
`practicable to reduce the diameter of the cylindrical
`drum 14 which in turn enables a reduction in both the
`size and power of the electric motor 104 and gear box
`106. Thus, in a prefered embodiment the hollow
`cylinder 88 has a diameter of 0.125 metres. The
`overall reduction in the size of the winch 10 enables
`it to be both manufactured and installed at a reduced
`cost. At the same time the described winch is capable
`of operating in a limited space environment which
`until now has not been practicable.
`
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`9 -
`
`It will be apparent to those skilled in the art
`that the longitudinal movement of the cylindrical drum
`14 and its associated drive means 18 may be
`accomplished by some means other than the rotation of
`an ACME screw threaded member such as that described
`above. For example, the drive for this longitudinal
`movement may be provided directly from the electrical
`motor 104 by way of a second output shaft from the
`bear box 106 or from an additional motor (not shown).
`Likewise, it will be apparent that the
`synchronisation between the rotation of the
`cylindrical drum 14 and the longitdudinal movement of
`the carriage 36 may be achieved in some way other than
`by way of a drive chain 116. For example, this
`synchronisation could be achieved by use of a timing
`belt or else by causing the rotational movement of the
`shaft 72 to be transmitted to the ACME screw threaded
`member 58 by way of one or more intermeshing gear
`wheels.
`
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`- 10 -
`
`CLAIMS
`
`A winch comprising a frame, a carriage
`1.
`adapted for movement with respect to the frame, a
`cylindrical drum mounted on the carriage for rotation
`with respect to the carriage about an axis extending
`generally axially of the drum, a cable attached to the
`drum and adapted to be wound around a circumferential
`surface thereof, drive means mounted on the carriage
`for rotating the drum about said axis, and means for
`moving said carriage with respect to the frame in a
`linear direction axially of the drum such that upon
`each rotation of the drum said drum moves axially
`relative to the frame by a distance equal to that
`separating adjacent turns of the cable when measured
`parallel to the drum axis.
`
`A winch in accordance with claim 1, wherein
`2.
`said means for moving said carriage comprises a member
`mounted to the carriage for rotation with respect
`thereto and in threaded engagement with the frame, and
`means for rotating said member so as to move said
`carriage with respect to the frame.
`
`A winch in accordance with claim 1, wherein
`3.
`said means for moving said carriage comprises a member
`mounted to the frame for rotation with respect thereto
`and in threaded engagement with the carriage, and
`means for rotating said member so as to move said
`carriage with respect to the frame.
`
`A winch in accordance with claim 2 or claim
`4.
`3, wherein said means for rotating said member
`comprises geared means rotatably interconnecting said
`drum and said member.
`
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`- 11 -
`
`5.
`said
`
`A winch
`geared means
`
`in accordance with claim
`includes a drive chain.
`
`4 I
`
`wherein
`
`6.
`said
`
`A winch
`geared means
`
`in accordance with claim
`includes a timing belt.
`
`5
`
`4,
`
`wherein
`
`7.
`said
`gear
`
`A winch
`geared means
`wheels.
`
`wherein
`in accordance with claim
`4 I
`includes one or more intermeshing
`
`A winch in accordane with claim 1, wherein
`8.
`said means for moving said carriage comprises
`additional drive means and means for synchronising the
`movement of the carriage with the rotational movement
`of the drum.
`
`A winch in accordance with claim 1, wherein
`9.
`the drive means for rotating the drum also serves to
`move the carriage with respect to the frame, the winch
`further comprising means for synchronising the
`movement of the carriage with the rotational movement
`of the drum.
`
`A winch in accordance with claim 1, wherein
`10.
`a helical groove is provided in the circumferential
`surface of the drum and the means for moving the
`carriage is such that upon each rotation of the drum
`said drum moves axially relative to the frame by a
`distance equal to the pitch of the groove.
`
`A winch substantially as herein described
`11.
`with reference to the accompanying drawings.
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`

`
`Patents Act 1977
`aminer's report to the Comptroller under Section 17
`(fhe Search report)
`
`'~
`
`Relevant Technical Fields
`
`(i) UK Cl (Ed.N)
`
`BBB (BCDD, BCDF)
`
`(ii) Int Cl (Ed.6)
`
`B66D
`
`Databases (see below)
`(i) UK Patent Office collections of GB, EP, WO and US
`patent specifications.
`
`Application number
`GB 9423979.5
`
`Search Examiner
`M DAVEY
`
`Date of completion of Search
`21NOVEMBER1995
`
`Documents considered relevant
`following a search in respect of
`Claims :-
`1TO11
`
`(ii)
`
`Categories of documents
`
`X:
`
`Y:
`
`A:
`
`indicating
`Document
`inventive step.
`
`lack of novelty or of
`
`P:
`
`Document indicating lack of inventive step if
`combined with one or more other documents of the
`same category.
`
`Document indicating
`and/or slate of the art.
`
`technological background
`
`E:
`
`&:
`
`Document published on or after the declared priority
`filing dale of the present
`date but before
`the
`application.
`
`Patent document published on or after, but with
`priority date earlier than, the filing date of the present
`application.
`
`Member of the same patent family; corresponding
`document.
`
`Category
`
`Identity of document and relevant passages
`
`Relevant to
`claim(s)
`
`x
`
`x
`
`x
`
`x
`
`x
`
`x
`
`GB 2271973 A
`
`GB 2183212 A
`
`GB 2158032 A
`
`GB 714071
`
`EP 0043367 A
`
`us 4972778
`
`(SUPERWINCH LTD) see drum 6 on
`carriage 10
`
`1
`
`(HANDLING CONSULTANTS) see
`movable frame or carriage 2 in
`Figures 1 and 2
`
`1, 2, 4, 5, 9,
`10
`
`(BRITISH NUCLEAR FUELS) see drum
`assembly movable by rollers 9, 10
`
`1, 2, 9, 10
`
`(KING) see carriage 19 movable by
`drum groove and cooperating block 23
`
`1, 2, 9, 10
`
`(ROSENDAHL) see wheeled frame 2
`supporting drum 7
`
`1, 8
`
`(SUOMINEN) see carriage 2 in Figure 2 1,2,9,10
`and threaded shaft 20
`
`Dalabases:The UK Patent Oflicc database comprises classified collections of GB, EP, WO and US patent specifications as outlined
`periodically in the Official Journal (Patents). The on-line databases considered for search are also listed periodically in the Official Journal
`(Patents).
`
`T4 - 24937
`15 of 15
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