WO2005073122A1 - Appareil de conversion de couple - Google Patents

Appareil de conversion de couple Download PDF

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Publication number
WO2005073122A1
WO2005073122A1 PCT/AU2005/000134 AU2005000134W WO2005073122A1 WO 2005073122 A1 WO2005073122 A1 WO 2005073122A1 AU 2005000134 W AU2005000134 W AU 2005000134W WO 2005073122 A1 WO2005073122 A1 WO 2005073122A1
Authority
WO
WIPO (PCT)
Prior art keywords
input
torque
output
gear
converting
Prior art date
Application number
PCT/AU2005/000134
Other languages
English (en)
Inventor
Kevin Arthur Dein
Original Assignee
Xact-Design & Engineering Pty Ltd
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
Priority claimed from AU2004900455A external-priority patent/AU2004900455A0/en
Application filed by Xact-Design & Engineering Pty Ltd filed Critical Xact-Design & Engineering Pty Ltd
Priority to EP05706218A priority Critical patent/EP1718557A1/fr
Priority to CA002560541A priority patent/CA2560541A1/fr
Priority to AU2005209335A priority patent/AU2005209335A1/en
Publication of WO2005073122A1 publication Critical patent/WO2005073122A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B17/00—Hand-driven gear-operated wrenches or screwdrivers
    • B25B17/02—Hand-driven gear-operated wrenches or screwdrivers providing for torque amplification
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B17/00—Hand-driven gear-operated wrenches or screwdrivers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/0078—Reaction arms
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/001—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion convertible for varying the gear-ratio, e.g. for selecting one of several shafts as the input shaft

Definitions

  • the present invention relates to apparatus for converting torque and especially, but not exclusively, to apparatus for converting a relatively small input torque into a greater output torque.
  • apparatus for converting torque In many applications, especially where a torque is applied manually using a hand tool, difficulty is experienced in attempting to provide adequate torque.
  • One application of conveniently converting a lower input torque to a higher output torque is to. allow apparatus or machinery which could not previously be manually driven by application of force in a single rotary motion, to be more easily driven.
  • apparatus for converting torque so that a relatively small input torque is converted to a greater output torque including: an input portion adapted to receive an input torque; an input gear connected to the input portion; an output gear; and an output portion, adapted to provide an output torque, connected to the output gear, wherein the input gear interacts directly with the output gear.
  • an apparatus for converting torque so that a relatively small input torque is converted to a greater output torque including: an input portion adapted to receive an input torque; an input gear connected to the input portion; an output gear; and an output portion, adapted to provide an output torque, connected to the output gear, wherein the output gear is directly connected to the output portion and unable to rotate with respect thereto.
  • the input portion is adapted to be directly rotated by a manually operated tool.
  • the input portion may be rotated by other means, for example, a servomotor, which may provide a predetermined torque.
  • the input portion is unable to rotate relative to the input gear.
  • the apparatus includes an interior cavity in which the input gear is located.
  • the interior cavity is defined at least partially by the output gear.
  • the apparatus for converting torque includes a plurality of input portions, which are connected to respective input gears .
  • each of the input gears interacts with the output gear.
  • the input gear(s) is (are) retained in position relative to a housing portion of the apparatus.
  • apparatus for converting torque so that a relatively small input torque is converted to a greater output torque including: a first input portion adapted to receive an input torque; a first input gear connected to the first input portion; a second input portion adapted to receive an input torque; a second input gear connected to the second input portion; an output gear; and an output portion adapted to provide an output torque, connected to the output gear, wherein a given input torque applied to the first input portion provides a greater output torque at the output portion than does the same torque applied to the second input portion.
  • at least one of the first and second input portions is adapted to output a torque when an input torque is input into the other of the first and second input portions.
  • the output portion is also adapted to receive an input torque, causing an output torque at the or each input portion.
  • the apparatus for converting torque further includes a third input portion adapted to receive an input torque, and a third input gear connected to the third input portion, wherein a given input torque applied to the third input portion provides a greater output torque at the output portion than does the same torque applied to the first or second input portion.
  • at least one of the input portions is adapted to be directly rotated by a manually operated tool.
  • the input portions are unable to rotate relative to their respective input gear.
  • the input portion (s) and input gear(s) are parts of an input gear member.
  • the output gear is unable to rotate relative to the output portion.
  • the output portion and output gear are parts of an output gear member .
  • the input gear(s) is (are) generally cylindrical.
  • the or each input gear includes a number of teeth on an external surface thereof.
  • the output gear is generally cylindrical.
  • the output gear includes a number of teeth on an internal surface thereof.
  • the apparatus includes an interior cavity in which the input gear (s) is (are) located.
  • the interior cavity is defined at least partially by the output gear .
  • the output gear has an axis of rotation and the output portion is located generally radially inwardly of the output gear.
  • a flange portion extends between the output gear and the output portion.
  • a direct drive input portion for directly driving the output portion.
  • the, or at least one of the input gear(s) drives at least one supplementary drive gear, which acts with the input gear to drive the output gear.
  • at least one idler gear between said input gear and said supplementary drive gear.
  • said idler gear serves to provide a complementary direction of rotation of the input gear and the supplementary drive gear.
  • the input gear is retained in position relative to a housing portion of the apparatus.
  • the housing portion is an input end housing portion.
  • the input gear is journalled in the housing portion.
  • the input gear may be journalled relative to a location member.
  • the location member may be within the output gear.
  • the input gear(s) is (are) rotatable and retained in position relative to the housing portion of the apparatus.
  • the apparatus includes at least one portion for attachment of a bracing member for bracing at least a portion of the torque multiplier against rotation in use.
  • the apparatus includes at least one socket for receipt of an attachment portion of a bracing member.
  • the at least one socket includes a cavity ' formed in the housing portion of the apparatus.
  • the socket may be formed separately and attached to the housing portion of the apparatus.
  • the input portions are adapted to receive tools of different sizes.
  • the output portion of the apparatus may be used to receive an input torque, causing an output torque at the or each input portion.
  • the apparatus is housed in a drum, the drum including attachment means for attaching a base to the drum.
  • the apparatus including: a mounting plate for mounting to the device; a pivot coupling; a cam mounted to the mounting plate via the pivot coupling; and a force transmission member which includes a cam following surface, wherein the force transmission member is for connection to a part of the device which requires reciprocal motion as an input; and wherein, in use, a torque applied to the cam causes movement of the force transmission member suitable for providing reciprocal motion as an input to the device .
  • the cam is substantially circular.
  • the cam is substantially disc-shaped.
  • the cam rotates eccentrically.
  • the cam following surface is generally circular.
  • the apparatus includes a cover plate.
  • the cover plate is, in use, located generally parallel to the mounting plate.
  • the cam and cam following surface are located, in use, between the mounting plate and the cover plate.
  • the apparatus includes supports, which extend between the cover plate and the mounting plate.
  • the apparatus further includes portions shaped suitably for attachment to the device.
  • the apparatus is adapted for use with a winch of the type of which requires reciprocal motion of a lever in order to operate the winch so as to pull a cable through the winch.
  • the mounting plate includes mounting members suitable for mounting an apparatus according to any of the first, second or third aspects of the invention to the apparatus.
  • apparatus for mounting a device to .a plate, the apparatus including: a plurality of brackets arranged to be spaced apart on the plate, at least one bracket including an aperture or slot for receipt of an elongate member therein; and an elongate member for said bracket, wherein the elongate member is adapted to be accommodated in the aperture or slot of the bracket and to be able to move along its own axis through the aperture or slot of the bracket; and wherein at least one fastening means is provided associated with the elongate member so that adjustment of the fastening means adjusts the axial position of the elongate member with respect to the bracket; and wherein the elongate member is adapted for engagement with a complementary portion on the device to be mounted so that when the elongate member is forced towards the apparatus by adjustment of the respective fastening member, the device is secured to the plate by the elongate member and the elongate member is retained in position by the fastening member.
  • the one or more elongate members each include a generally cylindrical threaded portion.
  • the one or more elongate members each include a section, which is square in cross-section, for insertion into a complementary square cross-section socket on the device.
  • the one or more fastening members are nuts.
  • the one or more fastening members are wing nuts.
  • rotation of the one or more fastening members about the axis of the associated elongate member causes axial movement of the fastening member.
  • the plate is a cover plate of a torque converter in accordance with the fourth aspect of the present invention.
  • the device is an apparatus in accordance with any one of the first, second or third aspects of the present invention.
  • an apparatus for converting torque so that an input torque is converted to a different output torque including: an input portion adapted to receive an input torque; an input gear connected to the input portion; an output gear; and an output portion, adapted to provide an output torque, connected to the output gear, wherein the input gear interacts directly with the output gear.
  • an apparatus for converting torque so that an input torque is converted to a different output torque including: an input portion adapted to receive an input torque; an input gear connected to the input portion; an output gear; and an output portion, adapted to provide an output torque, connected to the output gear, wherein the output gear is directly connected to the output portion and unable to rotate with respect thereto.
  • an apparatus for converting torque so that an input torque is converted to a different output torque including a first input portion adapted to receive an input torque, a first input gear connected to the first input portion, a second input portion adapted to receive an input torque, a second input gear connected to the second input portion, an output gear, and an output portion adapted to provide an output torque connected to the output gear, wherein a given input torque applied to the first input portion provides a greater output torque at the output portion than does the same torque applied to the second input portion.
  • FIG. 1 is a perspective view of an embodiment of apparatus for converting torque in accordance with an aspect of the present invention
  • Fig. 2 is an alternative perspective view of the embodiment of Fig. 1
  • Fig. 3 is a plan view and partial cross section of the embodiment of Figs. 1 and 2
  • Fig. 4 is a side elevation of the embodiment of Figs. 1 to 3
  • Fig. 5 is and alternative side elevation of the embodiment of Figs. 1 to 4
  • Fig. 6 is a cross sectional view on I-I of Fig.3
  • Fig. 7 is a cross sectional view on II-II of Fig.3
  • Fig. 1 is a perspective view of an embodiment of apparatus for converting torque in accordance with an aspect of the present invention
  • Fig. 2 is an alternative perspective view of the embodiment of Fig. 1
  • Fig. 3 is a plan view and partial cross section of the embodiment of Figs. 1 and 2
  • Fig. 4 is a side elevation of the embodiment of Figs
  • FIG. 16 is a plan view of an element, in the form of an output gear assembly of the embodiment of Figs. 1 to 9;
  • Fig. 17 is a side view of the element of Fig. 13;
  • Fig. 18 is a perspective view of the element of Fig. 13;
  • Figs. 19(a), 20(a) and 21(a) are side views of three respective input gear members of the embodiment of Figs. 1 to 9;
  • Figs. 19(b), 20(b) and 21(b) are respective plan views of the members of Figs. 19(a), 20(a) and 21(a);
  • Figs. 19(c), 20(c) and 21(c) are respective perspective views of the members of Figs. 19(a), 20(a) and 21(a);
  • Fig. 19(c), 20(c) and 21(c) are respective perspective views of the members of Figs. 19(a), 20(a
  • FIG. 22 is a schematic side view showing the inside of an embodiment of apparatus for converting torque in accordance with an aspect of the present invention, connected to a winch;
  • Fig. 23 is a schematic side view showing the outside of the embodiment of Fig 22 with the torque converter held in place;
  • Fig. 24 is a schematic cross section corresponding to XII-XII of Fig 23;
  • Figs. 25 and 26 show alternative structures for an element shown in Figs. 23 and 24;
  • Fig. 27 is a schematic cross section of an alternative embodiment according to an aspect of the invention;
  • Fig. 28 is a plan view in partial cross section of Fig. 27;
  • Fig. 29 is a cross section of an apparatus of an alternative embodiment according to an aspect of the invention;
  • FIG. 30 is a cross section of the apparatus of Fig. 29 illustrating a further use of the apparatus
  • Fig. 31 is a cross section of the apparatus of Fig. 29 illustrating another use of the apparatus
  • Fig. 32 is a cross section of the apparatus of Fig. 27 illustrating an alternative use of the apparatus
  • Fig. 33 is a schematic cross section of an alternative embodiment according to an aspect of the invention including a vertically extending socket
  • Fig. 34 is a plan view of Fig. 33
  • Fig. 35 is a side view of Fig. 33
  • Fig. 36 is a schematic cross section of an alternative embodiment according to an aspect of the invention including a radially extending socket
  • Fig. 37 is a plan view of Fig. 36
  • FIG. 38 is a schematic cross section of an alternative embodiment according to an aspect of the invention including a single input gear member, which acts as a sun gear;
  • Fig. 39 is a plan view of Fig. 38;
  • Figs. 40a and 40b are schematic cross sections of an alternative embodiment according to an aspect of the invention;
  • Figs. 41a and 41b are schematic cross sections of alternative embodiments according to Figs. 40a and 40b, further including a direct drive input;
  • Fig. 42 is a schematic cross section of an alternative embodiment according to an aspect of the invention;
  • Fig. 43 is a plan view in partial cross section of Fig. 42;
  • Fig. 44 is a plan view in partial cross section of an alternative embodiment of Fig. 42 and 43;
  • Fig. 52 is a schematic cross section of an alternative embodiment according to an aspect of the invention including a selectable friction drive mechanism
  • Fig. 53 is a plan view of an alternative embodiment according to an aspect of the invention including a friction drive mechanism
  • Fig. 54 is a schematic cross section of an alternative embodiment according to Fig. 52 further including a direct drive input
  • Fig. 55 is a schematic cross section of an alternative embodiment according to Fig. 52 adapted for use with wheel nuts
  • Figs. 56 to 64 are plan views of alternative gear arrangements according to embodiments of the invention
  • Fig. 65 is a schematic cross section of an alternative embodiment according to the invention including two torque multiplication stages
  • Fig 66 is a plan view of a possible gear arrangement for the torque multiplier of Fig. 65
  • 67 is a schematic cross section of an alternative embodiment according to the invention including three torque multiplication stages
  • Fig. 68 is a schematic cross section of an alternative embodiment according to the invention including four torque multiplication stages
  • Figs. 69a and 69b are a schematic cross section and plan view respectively of an alternative torque multiplier including two torque multiplication stages
  • Fig 70 is a plan view of a possible gear arrangement for the second stage of a torque multiplier
  • Fig. 71 is schematic cross section of an alternative embodiment according to the invention including two torque multiplication stages and single direction friction drives
  • Figs. 72a through 72e show schematic cross-sections of alternative embodiments according to the invention in the form of a spanner and torque multipliers for use in combination with the spanners
  • Fig. 74 is a schematic cross section of an alternative embodiment according to the invention in the form of a spanner including a locking member
  • Fig. 75 is perspective view of an alternative embodiment according to the invention
  • Fig. 76 is perspective cross sectional view of an alternative embodiment according to the invention
  • Fig. 77a is a semi-transparent view of an alternative embodiment according to the invention
  • Figs. 77b to 77f show various cross-sectional views of the embodiment of Fig. 77a.
  • a preferred embodiment of an apparatus for converting torque in accordance with an aspect of the present invention is in the form of a torque multiplier, generally designated 1.
  • the torque multiplier is generally cylindrical in form, in this embodiment having a radius approximately equal to its axial length, and includes a generally cylindrical wall 3, an input end 5, shown uppermost in Figs. 1 and 2, and an output end 6, shown at the bottom in Figs. 1 and 2.
  • the input end 5 and the portion of the generally cylindrical wall 3 which is closer to the input end 5, are formed largely by a generally half-cylindrical input end housing 30.
  • the output end 6 and the portion of the generally cylindrical wall 3 which is closest to the output end 6, is formed by a generally half-cylindrical output end housing 40.
  • an input end housing 30 is provided in the form of a disc-like plate, having a thickness about half as great as its radius.
  • the input end housing 30 has a generally planar, radially extending, input end surface 30A, and an axially short generally cylindrical surface 30B which forms an input end part of the generally cylindrical wall 3.
  • the input end housing 30 has first to fourth axially oriented generally circular apertures 31 to 34, respectively, provided therethrough.
  • the output end housing 40 includes a generally circular, generally planar, radially extending, end housing portion 40A, which has a generally circular aperture 42 provided centrally therein.
  • the output end housing 40 further includes an axially short generally cylindrical end housing portion 40B, which forms an output end part of the generally cylindrical wall 3.
  • the input end housing 30 and output end housing 40 are substantially rigidly connected together by interaction of crenulated portions 49A, 49B, 49C, which extend axially from the generally cylindrical output end housing portion 40B, with respective complimentary recessed portions 39A, 39B, 39C in the generally cylindrical surface 30B of the input end housing 30 (as shown, for example, in Fig. 12) .
  • the crenulated portions are secured to the recessed portions 35 by suitable fasteners such as grub screws 48A, 48B, 48C (shown in Fig. 8) .
  • suitable fasteners such as grub screws 48A, 48B, 48C (shown in Fig. 8) .
  • the direct drive input portion 14 (Fig. 1) includes a square drive cavity 14A, for receipt of a driving portion of a driving tool such as a square drive ratchet wrench, suitable lever, or the like.
  • the direct drive input portion 14 forms part of an output gear member 24 of the torque multiplier (Figs. 16 to 18) which further includes an axially extending central shaft 17 which extends the axial length of the torque multiplier 1 and terminates at the output end in an output portion 16.
  • the output portion 16 extends out of the circular end housing portion 40A, through the central circular aperture 42 (Fig 13) , and, in this embodiment, terminates in a drive portion, which is square in radial cross section so that it can conveniently be used to drive tools with a suitable square-drive connection. Because the direct drive input portion 14 and the output portion 16 are directly and rigidly connected, it will be appreciated that rotation of the direct drive input portion 14 by a given angular displacement will result in the same angular displacement of the output portion 16.
  • a flange 18 extends radially outwardly, substantially to the inside of the cylindrical end housing portion 40B of the generally cylindrical wall 3.
  • a cylindrical output gear 19 Extending axially, and, in use, towards the input end 5 of the torque multiplier 1, from the generally circular periphery of the flange 18, is a cylindrical output gear 19, which has a plurality of output gear teeth 26 on a radially inner surface thereof.
  • the radius of the output gear 19 is only slightly smaller than the radius of the torque multiplier 1, and the axial length of the output gear 19 is only slightly smaller than the axial distance between the flange 18 and the input end housing 30.
  • the flange 18, output gear 19 and gear teeth 26 are parts of the output gear member 24.
  • First to third input gears, 21 to 23 respectively, are provided for interaction with the output gear 19.
  • Each of the input gears 21 to 23, has a plurality of input gear teeth 25, which interlock, and drive (or could, if an input torque were applied to the output portion 16, be driven by) the output gear teeth 26.
  • Figs. 16 the radius of the output gear 19 is only slightly smaller than the radius of the torque multiplier 1
  • the axial length of the output gear 19 is only slightly smaller than the axial distance between the flange 18 and the input end housing 30.
  • the flange 18, output gear 19 and gear teeth 26 are parts of the output gear member 24.
  • First to third input gears, 21 to 23 respectively, are provided for interaction with the
  • the input gears 21 to 23, are formed as parts of respective first to third input gear members 27, 28, 29 and are thus rigidly connected to and in this embodiment formed integrally with, respective generally cylindrical first, second and third torque input portions, 11, 12, 13.
  • first, second and third torque input portions, 11, 12, 13 extend axially through the respective first, second and third apertures 31, 32, 33 (Fig 10) of the input end housing 30.
  • the first, second and third torque input portions, 11, 12, 13 each include a respective square drive cavity 11A, 12A, 13A, for receipt of a driving portion of a driving tool such as a square drive ratchet wrench, suitable lever, or the like.
  • Each input gear member 27, 28, 29 is retained against radial movement relative to the input end housing 30 by being journalled in the respective aperture 31, 32, 33 of the input end housing 30 and is retained against axial movement by engagement of respective radially extending external shoulders 11B, 12B, 13B, of the input gear members 27, 28, 29 with respective internal shoulders 31B, 32B, 33B of 30 the apertures 31, 32, 33 through which they extend.
  • Each input gear member 27, 28, 29 is further rotatably retained relative to the other input gear members, and against significant radial movement relative to the output gear 19 and the central shaft 17, by location of a respective axially extreme, output end, circular lug (not shown) which is, in use, located in a respective aperture, e.g. of a location plate 20 (Fig 9).
  • the location plate 20 is located between the input gears 21, 22, 23 and the flange 18, and can rotate relative to the output gear member 24.
  • the location plate 20 thus includes a number of apertures, namely one to journal an end lug of each of the (in this embodiment three) input gears 21, 22, 23 and one to allow the central shaft 17 to pass therethrough.
  • the location plate 20 is optional, since the input gear members are securely journalled in the axially thick input end housing 30.
  • a location plate (or other location member) may be of greater necessity. As is best illustrated in Figs.
  • each of the input gears 21, 22, 23 has a different number of input gear teeth 25, and in each case the number is considerably less than the number of output gear teeth 26, so that a mechanical advantage, or torque multiplication, proportional to the ratio of the number of teeth will be provided (although some loss due to friction occurs) upon rotation of the input portions 11, 12, 13.
  • a user may therefore select direct drive (torque multiplication of unity) or a multiplication of three, four or six (excluding frictional losses) by applying torque to the direct drive 14, or the first second or third torque input portions 11, 12, 13 respectively.
  • direct drive torque multiplication of unity
  • a multiplication of three, four or six excluding frictional losses
  • the first, second and third input gears 21, 22, 23 have twelve, eight and six teeth respectively, and the output gear 19 has 36 teeth.
  • the input and output portions of the apparatus of Figs. 1 to 21 may be used in the opposite role, that is the apparatus may be driven from the output portion to the input portion, in a case where the apparatus is to be used as a speed tool rather than a torque multiplier.
  • the apparatus may also be driven from one of the inputs to another one of the other inputs .
  • the torque multiplier 1 other than on direct drive
  • the apparatus itself must be braced against rotation. This bracing may be provided by connection of a suitable bracing member (not shown) to one of the sockets 36, 37, 38.
  • a torque multiplier is conveniently attachable to other apparatus by use of such connections, in a way which would not be practicable using a permanently attached bracing bar.
  • a torque converter for converting an input torque into a suitable form for driving apparatus which requires reciprocal motion as an input.
  • a preferred application of the torque converter 50 is to drive an apparatus often known as a TIRFORTM, GRIPHOISTTM or GREIFZUGTM machine.
  • Such machines are a type of winch or hoist which uses reciprocating motion (indicated by the arrow in Fig. 22) of a manually operated lever 61 to effectively pull a wire rope 62 through the TIRFORTM machine 60 (or, alternatively, to pull the TIRFORTM machine 60 along a wire rope 62) .
  • TIRFORTM machines are strenuous to use, since in order to operate under large loads a considerable force must be applied to move the lever 61, often in an inconvenient position.
  • the apparatus includes a mounting plate 51, which is securely attached to the machine 60.
  • a cam 52 which in this embodiment is substantially circular and mounted eccentrically about a pivot coupling 53.
  • the pivot coupling 53 includes a connection portion (not shown) , such as, for example, a square drive socket, and is rigidly connected to the cam 52, so that rotation of the pivot coupling 53 causes the cam 52 to rotate eccentrically.
  • a connection portion such as, for example, a square drive socket
  • the ring fitting 54 includes, at the radially inner part thereof, a substantially circular cam following surface 56 for engagement with the cam 52.
  • the force transmission member 55 has a second end 57, which, in use, is pivotally attached to the lever 61 of the TIRFORTM machine 60.
  • the force transmission member 55 also includes an intermediate portion 58, between the first and second ends thereof, and where the intermediate portion 58 connects to the ring fitting 54, the intermediate portion 58 includes somewhat concave portions 58A to allow compact design while helping to avoid undesirable interaction or collision of the intermediate portion 58 with any edge of the apparatus .
  • a torque multiplier of the general type illustrated in Figs 1 to 9 is securely (albeit indirectly) connected to the mounting plate 51, and such an arrangement is illustrated schematically in Fig. 23.
  • Fig. 23 shows schematically a torque multiplier of the general type illustrated in Figs 1 to 9, secured to a cover plate 70.
  • the cover plate 70 is, in use, secured to the mounting plate 51 by any suitable means, and a preferred arrangement is shown schematically in Fig. 24, and will be described below.
  • the torque multiplier 1 is secured to the cover plate 70 by first, second and third securing members 71, 72, 73, respectively.
  • Each securing member 71, 72, 73 is elongate in form and includes a threaded shaft portion (72A, 73A in Fig. 24) which extends from a first end of the securing member approximately two thirds along the securing member, and which, in use, is distal from the torque multiplier 1.
  • Each securing member 71, 72, 73 also includes a square cross section portion (72B, 73B in Fig.
  • each securing member 71, 72, 73 is secured to the cover plate 70, by retention in a respective bracket, 74, 75, 76.
  • the brackets 74, 75, 76 are preferably small plates upstanding from the cover plate 70, each including an aperture through which the respective securing member extends.
  • the apertures may be circular apertures, as illustrated in Fig. 25, or may be open slots 75A in order to facilitate insertion of the securing members, as illustrated in Fig. 26.
  • each securing member 71, 72, 73 is adjustable by operation of one or more associated nuts 78, which may be wing nuts, and which cooperate with the threaded portions of the securing members 71, 72, 73 and which may bear against the respective bracket 74, 75, 76 in order to position the securing means 71, 72, 73. It will be appreciated that rotation of one of the nuts 78 causes axial movement of the nut 78 relative to the securing member to which the nut 78 is attached.
  • the securing member 71, 72, 73 is inserted in a socket of the torque multiplier and also in the aperture or slot of an associated bracket 74, 75, 76, then a given nut 78 can be rotated so that it abuts its respective bracket 74, 75, 76, at which its axial movement is stopped by the bracket 74, 75, 76.
  • the securing member is then effectively held in compression between the bracket/nut and the torque multiplier.
  • Providing securing members on opposing sides of (or suitably spaced around) the torque multiplier results in convenient and secure location of the torque multiplier.
  • the apparatus 50 includes first and second side supports 81, 82 which, in use, extend along the sides of the TIRFORTM machine 60 and support the mounting plate 51 and the cover plate 70.
  • the side supports 80, 81 are spaced apart so that a given- TIRFORTM machine may fit therebetween.
  • TIRFORTM machines typically have small flanges 64 running along their edges, and the side supports 80, 81 include, at their extremes, respective shoulders 82, 83 for engagement with the flanges 64.
  • the shoulders 82, 83 are secured to the flanges by suitable fasteners 85, 86, shown schematically in Fig. 24, such as bolts, and, as seen in Fig. 24, corresponding apertures are provided in the shoulders 83, 84 and in the flanges 64.
  • access apertures are provided in the side supports 81, 82 in order to allow access to fasteners, such as nuts, which may be located, in use, between the flanges 64 and the mounting plate 51.
  • fasteners such as nuts
  • This type of fastening is economical, secure, reversible, and requires minimal modification of the TIRFORTM machine, although, of course, alternative means of securing the apparatus 50 to the TIRFORTM machine 60 including welding, clamping or the like may be suitable alternatives depending on the circumstances .
  • the mounting plate 51 extends between the side supports 81, 82 and effectively supports the cam 52 and separates the cam 52 from the TIRFORTM machine 60.
  • the pivot coupling 53 is journalled in the mounting plate 51.
  • the side supports 81, 82 provide respective upstanding rim portions 91, 92 and respective inwardly extending ledge portions 93, 94 to support and locate the cover plate 70.
  • the upstanding rim portions 91, 92 extend in the direction of the thickness of the cover plate 70 and are dimensioned so that the cover plate 70 may sit flush between them.
  • the ledge portions are dimensioned so that appropriate fasteners (such as bolts -not shown) may extend through the ledge portions 93, 94 and the cover plate 70 in order to secure the cover plate 70.
  • the ledge portions 93, 94 are provided with means to allow such fastening, such as threaded apertures, captive nuts, or the like.
  • connection between the second end of the force transmission member 55 and the lever 61 may include a cam attached to the lever 61 and a cam follower forming the second end of the force transmission member 55.
  • the transmission member 55 may be connected to the lever 61 at a selected axial position on the lever 61 to provide a selected mechanical advantage.
  • the torque converter 50 especially in combination with the torque multiplier 1, provides a convenient and useful means of converting a machine such as a TIRFORTM machine from a machine which is labour intensive and possibly cumbersome to operate using a reciprocal action, into one which is much easier and more convenient to operate using a rotary action.
  • a powered driving device for example, a power tool such as an electric drill, might be suitable for applying the required torque to the input of the torque multiplier 1.
  • Fig. 27 and subsequent figures show embodiments of torque multipliers in accordance with one or more aspects of the present invention that are variations or alternative embodiments to the embodiment illustrated in Figs. 1 to 9. Similarities with the embodiment of Figs. 1. to 9 will be apparent to those skilled in the art and will not be discussed in detail.
  • Fig. 27 is a cross-section of a torque ' multiplier generally designated 101 with a housing 130 in the form of a casing, rather than including an input end housing as great in axial extent as the input end housing 30 of the torque multiplier 1 of Figs. 1 to 9.
  • An input end 130A of the housing 130 includes one or more apertures 131 to allow respective input gear members 127 to extend from respective torque input portions 111 thereof through the input end housing 130A so that respective input gears 121 can interact with an output gear 119.
  • the torque converter 101 includes a central output cylinder 117, which may be regarded as analogous to the central shaft 17 of the embodiment of Figs 1 to 9, but which is generally cylindrical in shape so that a continuous bore 135 extends through the centre of the torque multiplier 101. This enables the torque multiplier 101 to be used to operate fasteners such as bolts on long threaded shafts, such as those found in some designs of heat exchanger.
  • the torque multiplier 101 may effectively travel along the shaft with the fastener, with the shaft extending through the bore 135.
  • the cylinder 117 includes an input end at which the central bore is square in cross-section to allow it to be driven by a square drive tool, and an output end at which the bore 135 is hexagonal in cross—section in order to allow engagement with a fastener such as a nut, or an adaptor for connection to such a fastener.
  • the torque multiplier 101 further includes a location member 120 in which input gear members 127 are journalled and, in this embodiment, the location member 120 includes an output end location plate 120A which includes apertures in which end lugs of the input gear members 127 are journalled and an input end plate 120B which includes portions which may bear against and assist in the location of a part of the input gear member 127 intermediate a torque input portion 111 and the input gear 121 of each respective input gear member 127.
  • the input end portion 130A of the casing 130 is not sufficiently axially thick to include socket apertures therein.
  • Sockets 137 are thus provided as generally cylindrical members having radially outwardly open bores which are square in cross- section provided therein although they could be of circular cross- section.
  • the sockets 137 are attached to the input end housing 130A by welding, or may be formed integrally therewith.
  • Fig. 28 is a plan view in partial cross-section of the embodiment of Fig. 27 in which first, second and third sockets 136, 137, 138 are shown, and in which location of first to third input gears 121, 122, 123, each providing a different number of teeth for interaction with the output gear 119, can be seen.
  • the torque multiplier 101 includes first and second supplementary input drive gears 171, 172 which are driven by the first input gear 121 via first and second idler gears 181, 182.
  • the supplementary input are driven by the first input gear 121 via first and second idler gears 181, 182.
  • ⁇ gears 171, 172 engage the output gear 119 and thus help to distribute the force applied to the output gear 119 when the first input gear 121 is driven.
  • the idler gears 181, 182 do not engage the output gear 119, but ensure that the input gear 121 and supplementary input gears 171, 172 rotate in the same direction in use.
  • the idler gears 181, 182, also allow the distribution of torque received by the first input gear 121 to be shared across the two supplementary input gears 171, 172 where a high input torque is provided, and/or a low number of teeth are provided on the gears.
  • the supplementary input gears 171, 172 and idler gears 181, 182 are journalled in the location member 120, and do not extend outside the casing 130.
  • the second and third input gears 122, 123 drive the output gear 119 only, and do not have associated idler and supplementary drive gears .
  • the casing 130 is braced against rotation by one or more bracing members located in one or more of the sockets 136, 137, 138, and that the housing 130, input gears 121, 122, 123, location member 120, idler gears 181, 182 and supplementary input gears 171, 172 do not rotate about the axis of the torque multiplier 101 in use.
  • the output cylinder 117 and output gear 119 (which may be formed as a single element constituting an output member) do rotate in normal use of the torque multiplier. Fig.
  • FIG. 29 illustrates use of a torque multiplier 102 that is similar to the torque multiplier 101 in operating a nut 192 on' a threaded shaft 192.
  • the torque multiplier of Fig. 29 can be specifically designed to drive any size of nut allowing the threaded shaft 192 to pass through the tool. This tool can travel down the threaded shaft 192, as the nut 191 is moved down the shaft 192, which makes it particularly suitable for use with heat exchanger head plates, as discussed above.
  • i Fig. 30 illustrates use of a torque multiplier 103 similar to the torque multipliers 101, 102 in which a socket adaptor 150 is used to drive a large nut 160 on a threaded shaft 161.
  • the socket adaptor 150 includes a driven portion 152, which is generally cylindrical but which has an outer surface which is hexagonal in cross section for engagement with the output of the torque multiplier 103, and which is relatively radially small in extent and which has a bore therethough for passage of the threaded shaft 161.
  • the socket adaptor 150 further includes a driving portion 154, which has an internal surface 156 which defines a cavity which is hexagonal in cross-section in order to accommodate the nut 160.
  • the driven portion 152 and driving portion 154 are connected by a radially extending flange portion 153.
  • Fig. 31 shows the torque multiplier 103, in use, with a drive adaptor 162.
  • the drive adaptor is provided in order to provide a square drive output for the torque multiplier 103.
  • the driver adaptor 162 is an elongate member, which is locatable in the drive cylinder of the torque adaptor 103.
  • the drive adaptor 162 includes a driven portion which is hexagonal in cross-section and dimensioned to co-operate with and to be driven by the drive cylinder of the torque adaptor 103, and further includes a first square drive output 164, which is square in cross-section and which provides a IH inch (approximately 32mm) drive at one end thereof and a second square drive output 165, which provides a I inch (approximately 38mm) drive.
  • the adaptor 162 is provided with ball detents for secure connection to the torque multiplier 103 and to sockets or other members that are to be driven. Also shown in Fig.
  • FIG. 31 is an alternative drive adaptor 166 which includes a central driven portion, an end portion which provides a 1 inch (approximately 25mm) drive 168 and a % inch (approximately 19mm) drive 169.
  • Fig. 32 shows schematically an alternative in which the torque multiplier 101 of Fig. 27 may be used to operate sockets via square cross-section drive blocks 198, which may be driven by what is nominally the drive or input portion of the output cylinder 117. It will be appreciated that an output socket, for example socket 199 in Fig. 32 can be driven on what is nominally the input side of the torque converter 101.
  • Figs. 33 to 35 show an alternative embodiment of a torque multiplier in accordance with one or more aspects of the present invention.
  • the torque multiplier generally designated 201, includes a first torque input portion 211 which is geared to provide a torque multiplication of approximately 3:1 and a direct drive input portion 214.
  • This embodiment of a torque multiplier 201 therefore differs from the previously illustrated embodiments by having one direct drive and only one geared, torque input.
  • This embodiment of a torque multiplier 201 further differs from some of the other described embodiments in that an outer cylindrical wall of an output gear member 224 provides the outer cylindrical wall of the torque multiplier 201 and a flange 218 which forms part of the output gear member 224 forms the output end of the housing.
  • a generally circular plate forms the input end housing 230 (Fig.
  • the retention member 240 has a first portion 240A, which extends from a central part of the input end housing to a periphery of the torque multiplier 201, a second portion 240B, which extends axially along the outside of the cylindrical portion of the output gear member 224, a third portion 240C, which extends diametrically across the flange 218 of the output gear member 224 and a fourth portion 240D, which extends axially from the output end of the torque multiplier to the input end of the torque multiplier along the cylindrical part of the output gear member 224, where it is attached to a socket 236.
  • the socket 236, input end housing 230, and retention member 240 do not rotate about the axis of the torque multiplier 201, but the output gear member 224 including the flange 218 and an output portion 216 do rotate about the axis of the torque multiplier 201.
  • Using the outer surface of the output gear member 224 as part of the housing of the torque multiplier 201 may be useful to minimise the weight of the device. It will be appreciated that the torque multiplier is reversible and could be driven from the output portion 216 which would result in a 1:3 ratio to the output at the first input portion 211.
  • Figs. 36 and 37 show an embodiment in which a socket 237 is provided extending radially from an external wall, formed by retention member 241.
  • Figs. 36 and 37 is generally analogous to the retention member 240 in Figs. 33 to 35, but is of slightly different configuration, while still extending a significant way around the outside of the torque multiplier and rigidly fixing the socket 237 to an input end housing 230A and rotatably retaining both to the output gear member 224A.
  • the embodiment of Figs. 36 and 37 has a single torque input 212, which will be understood by analogy with other embodiments described herein.
  • Figs. 38 and 39 shows schematically an embodiment having a single input gear member 213 which acts as a sun gear and which drives an output gear 244 via first and second planetary idler gears 251, 252 each of which drives respective first and second planetary drive gears 253 to 256.
  • the sun gear has a diameter of approximately 40% of the diameter of the output gear 244 giving a torque multiplication of approximately 2.5.
  • Fig. 40a shows schematically a torque multiplier in which a single off centre input gear member 261 engages an output gear 262 to give a torque multiplication of approximately 4.
  • An external toothed ring gear 263 is included concentric to and radially inside the output gear 262.
  • the ring gear 263 enables the input gear member to drive a supplementary drive gear 264 which also drives the output gear 262 and thereby helps to distribute the input force.
  • One or more generally annular location plates 265, 266, 267 are provided in order to locate the gears relative to each other.
  • the torque multiplier is reversible and could be driven from the output portion 216, the input portion then providing the output from the converter, which would result in a reversed ratio to that supplied by driving the single torque input 261.
  • Fig. 40b illustrates an embodiment similar to that of Fig. 40a but includes a direct drive input 268 functioning in the same manner described above with respect, for example, to Figs. 1 to 9.
  • Fig. 41a and 41b correspond to Figs.
  • Figs. 42 and 43 illustrate a further embodiment of a torque multiplier which will be understood with reference to the description of the embodiment of Figs. 27 and 28, although it will be appreciated that the embodiment of Figs. 42 and 43 has a central shaft 117b, which can be engaged from each axial side of the apparatus, rather than a drive cylinder (117 in Fig. 27) .
  • the torque multiplier is reversible and could be driven from the output portion 117b, which would result in a reversed ratio to that supplied by driving the torque input in Fig 42.
  • Fig. 44 illustrates a variation of the embodiment of Figs. 42 and 43 in that only a single socket 238 is provided.
  • Figs. 45a and 45b illustrate a further variation in which a socket 238A is provided extending radially from a cylindrical side of the torque multiplier.
  • Figs 46a and 46b correspond to the embodiment shown in Figs
  • FIG. 47 shows a further variation with three peripheral torque inputs 121, 122, 123 in addition to a central input 2628 and three sockets 2622, 2624, 2626 for bracing members, which are diametrically opposite the three peripheral inputs 121, 122, 123.
  • FIGs. 48 and 49 illustrate a torque multiplier having a single torque input portion 402 directly connected to a sun gear 401.
  • the sun gear 401 drives first, second and third idler gears 403, 404,
  • the planetary drive gears in turn drive an output gear 412, which, analogous to output gears in other embodiments, is rigidly connected to an output 416.
  • the ratio of teeth on the sun gear to the output gear is about 5.5:1, providing a corresponding torque multiplication.
  • the sun gear 401 is 18mm in diameter and has 12 gear teeth
  • first, second and third idler gears 403, 404, 405 have 24 teeth
  • the six planetary drive gears 406 to 411 have 12 teeth
  • the output gear 412 has approximately 66 gear teeth.
  • the sun gear 401, idler gears 403, 404, 405 and planetary drive gears 406 to 411 are retained in appropriate positions by first and second location plates 413, 414.
  • the purpose of the idler gears 403, 404, 405 is to correct rotation to correspond with the input rotation direction. Additionally, by having multiple idler gears 403, 404, 405, engaged with the input gear 401, and multiple planetary gears 406 to 411 engaged with each idler gear 403, 404, 405, the input force is distributed through multiple gears.
  • the input portion 402 is provided with an O-ring seal 415 in order to avoid entry of debris or fluid from the input side to the interior of the torque multiplier.
  • the input portion 402 is further provided with a square drive cavity 417, which extends in the axial direction of the torque multiplier, and also with a radial through-bore 418, in this embodiment in the form of a circular 13mm aperture.
  • the through-bore 418 allows the torque input portion to be driven by insertion of any appropriate lever or bar making the torque multiplier more flexible in operation than it would be if it were dependent upon provision of a square drive tool.
  • the apparent asymmetry in the sun gear 401 is intended to illustrate only the meshing of the teeth of the sun gear 401 with the teeth of the idler gear 404, and is not intended to indicate asymmetry in the gear.
  • Figs. 50 and 51 show a variation of the embodiment of Figs. 48 and 49 in which a torque input 419 is provided to directly drive one of the planetary drive gears.
  • Fig. 52 illustrates an embodiment of a torque multiplier in which a friction drive mechanism 420 is provided as part of the torque input portion 421. As shown in Fig. 53, the mechanism is of the type described in US Patent No. 3621739, the contents of which are hereby incorporated by reference.
  • Fig. 52 illustrates a variation of the embodiment of Fig. 52 and includes a direct drive input 422.
  • the direct drive input is a 1:1 ratio and the torque input portion 421 is a suitably higher ratio depending on the arrangement of the torque multiplier.
  • Fig. 55 illustrates a variation of the embodiment of Fig.
  • the wheel nut 425 could be of any type and is shown attached to a wheel hub 4240 and a wheel rim 4250 for completeness. Also shown is an extension bar 4230, which can be fitted to the output 423 in the case where there is a confined space in which to remove the nut 425.
  • the torque drive input 4290 includes a hole 4270 which is adapted to receive a bar or rotating tool [not shown] in order to turn the torque input drive 4290.
  • the torque drive input 4290 is hexagonal in cross-section, so that it can also be driven by a wheel brace or socket (not shown.).
  • the torque drive input 4290 further includes an O-ring seal 4260 in order to avoid entry of debris or fluid from the input side to the interior of the torque multiplier.
  • the torque multiplier is applied by placing the wheel nut 425 into cavity 423 or alternatively through the cavity of the extension bar 4230 (then the torque multiplier is applied to the extension bar) .
  • the torque drive input 4290 is then turned, preferably by using a wheel brace or bar [not shown] through hole 4270 in order to loosen the nut 425.
  • the direct drive 4280 may then be used to remove the nut 425 from the wheel hub 4240 more quickly than would occur for the same number of turns of the torque input drive 4290.
  • the output 423 may be of various different sizes and/or different sized engaging portions or extensions, fitted to the output 423 can be used.
  • Figs. 56 to 64 show arrangements of driven gears and idler gears, which could be used in alternative embodiments of torque converters. Each of the embodiments in Figs. 56 to 64 includes a sun gear, generally designated 500.
  • the sun gear can conveniently be used to transmit motion from a cylindrical gear at one part of the torque multiplier interior to a cylindrical gear at another part of the torque multiplier interior, while minimising the number of intermediate gears, and allowing a direct drive or central shaft to pass through the interior of the sun gear.
  • This allows effective transmission of force in order to distribute the load and avoid or reduce wear and/or damage to the gears while conveniently allowing a central direct drive.
  • the number of' idler gears and supplementary drive gears may be selected to provide appropriate load distribution for the purpose of the tool and the materials from which it is made.
  • Figs. 56a and 56b illustrate an exemplary gear arrangement for a dual drive torque multiplier in order to provide equal load distribution for both forward and reverse direction of the drives.
  • the gear arrangement for the torque multiplier includes an internally toothed ring gear 5090 (106mm diameter) and an externally toothed sun gear 500 (54mm diameter) concentric with ring gear 5090.
  • Sun gear 500 is concentric with, and free to rotate around, a direct drive input 5010, which is integral with an output portion 5500, thereby providing a torque multiplication of 1:1.
  • the ring gear 5090 is also integral with the output portion 5500. As best seen in Fig.
  • the gear arrangement further includes an externally toothed drive (input) gear 5040 and two supplementary drive gears 5030, 5050 (all 20mm in diameter) , the teeth of which engage with the teeth of the ring gear 5090.
  • Drive gear 5040 is connected to a torque input 5020 having a torque multiplication of 5:1 to the output portion.
  • the gear arrangement further includes first and second intermediate planetary gears 5100, 5110 (each 20mm diameter) connected between the drive gears 5030, 5040 and 5050 and sun gear 500.
  • First intermediate planetary gear 5100 is connected between drive gears 5030, 5040 and sun gear 500 while second intermediate planetary gear 5110 is connected between drive gears 5040, 5050 and sun gear 500.
  • the input drive gear 5040 When the input drive gear 5040 is driven, it drives both the planetary gears 5100, 5110, which drive the sun gear 500. By driving the sun gear 500, the force from the input gear 5040 is spread to both the planetary gears 5100, 5110 equally, and to both supplementary drive gears 5030, 5050. Each of the supplementary drive gears 5030, 5050 also drives the ring gear 5090, hence the output portion. Due to the symmetry of the supplementary and planetary gears on either side of the drive gear 5040, equal distribution is obtained in both directions of rotation of the drive gear 5040. The planetary gears 5100, 5110 also provide directional correction so that input and output torques are in the same direction. Fig.
  • the gear arrangement for the torque multiplier includes the set up of internal gears described with reference to Figure 56 above, with the addition of a further planetary gear 5120, which is engaged with the sun gear 500 and two associated supplementary drive gears 5060, 5070, which are of equal size and are engaged between the ring gear 5090 and further planetary gear 5120.
  • the further planetary gear 5120 is provided axially opposite the drive gear 5040, and is driven via the sun gear 500 via its associated supplementary gears 5060, 5070.
  • the ring gear 5090 is also driven.
  • Fig. 58 illustrates an exemplary gear arrangement for a dual drive torque multiplier in order to proportion the drive load in both the forward and reverse directions.
  • the dimensions of the gears may be of any suitable size in order to provide the desired torque multiplication.
  • the gear arrangement includes the gear arrangement described with reference to Fig. 56 above; the elements of Fig. 57 shared with Fig 56 are also shared with this arrangement.
  • a single further supplementary drive gear 5060 is provided axially opposite the drive gear 5040.
  • the further supplementary drive gear 5060 drives the ring gear 5090 and is driven by the sun gear 500 via two equally sized planetary gears 5120, 5130 mounted between the further supplementary drive gear 5060 and the sun gear 500.
  • Fig. 59 illustrates an exemplary gear arrangement for a dual drive torque multiplier in order to provide equal load distribution.
  • the dimensions of the gears may be of any suitable size in order to provide the desired torque multiplication.
  • This arrangement includes a central sun gear 500, and a concentric, internally toothed, ring gear 5090.
  • Three planetary gears 5100, 5101, 5102 are positioned, engaged with the sun gear 500, at equal separations around the sun gear 500.
  • Each planetary gear 5100, 5101, 5102 is engaged with the ring gear 5090 via a pair of drive gears.
  • One of the drive gears 5040 is a primary drive gear, which receives drive input, while the others are supplementary drive gears.
  • the primary drive gear 5040 drives the ring gear 5090 and also the engaged idler gear 5100.
  • That idler gear 5100 drives the first supplementary drive gear 5030 (which drives the ring gear 5090) and also drives the sun gear 500.
  • the sun gear 500 drives the other idler gears 5101, 5102, which in turn drive the further supplementary drive gears 5050 to 5080, and thus the ring gear 5090.
  • the torque multiplier includes a sun gear 500, which assists to even out the tool action.
  • the dimensions of the gears may be of any suitable size in order to provide the desired torque multiplication.
  • the torque multiplication is 4:1, rather than the 5:1 shown in Fig. 56.
  • the relative sizes of the gears of Fig. 56 are altered, while the interaction of the gears remains the same.
  • the drive gears 5110, 5100 are approximately 25mm in diameter and the sun gear is approximately 54mm in diameter.
  • Figs. 63 and 64 illustrate exemplary gear arrangements for a dual drive torque multiplier. The dimensions of the gears may be of any suitable size in order to provide the desired torque multiplication .
  • the overall arrangement includes two arrangements as described with reference to Fig. 56 above, mounted diametrically opposite about the central sun gear 500, with the exception that only one of the two arrangements can be driven, the other acts only as a supplementary arrangement.
  • Fig. 65 illustrates a torque multiplier that includes two separate torque multiplication stages.
  • a first torque multiplication stage, indicated as stage 1 in Fig. 65 may have an arrangement of gears as illustrated in Fig. 66. The first stage shown in Fig.
  • a second stage, indicated stage 2 is in isolation functionally similar to embodiments of torque multipliers previously described. The output of the second stage is connected to the input of the first stage.
  • rotation of the second stage input will result in a two stage torque multiplication process so that if the first stage (sun gear based) torque multiplication has a multiplication factor of 5:1 and the second stage torque multiplication has a multiplication factor of 4:1, a total torque multiplication of approximately 20:1 will be achieved. It will further be appreciated that by using the first stage input drive 510, only the torque multiplication corresponding to the first stage will be achieved, so that in the illustrated embodiment, a user may select a torque multiplication of 20:1 or of 5:1. It will further be appreciated that the second stage torque multiplier could include a number of torque input portions and could provide a choice of torque multiplications, for example, 4:1, 5:1 and 6:1.
  • Fig. 67 illustrates a three stage torque multiplier.
  • the first and second stages each give a torque multiplication of 5:1 and the third stage gives a choice between a direct centre drive or torque inputs giving a 3:1 or 4:1 torque multiplication.
  • the first and third stages correspond to the first and second stages described in relation to Figs. 65 and 66 above, with the first stage being the same as the second stage.
  • the total torque multiplication for the three-stage device is selectably 25:1, 75:1 or 100:1. It will be appreciated that having two or more stages allows the torque multiplier to also act as a variable speed tool. For example, the user could apply the torque multiplier to a nut that is required to be removed from a bolt at a ratio of 100:1 in order to initially displace the nut, then switch to a ratio of 75:1 to move the nut along the thread of the bolt before switching to 25:1 as the nut is reaching the end of the bolt, and the required torque is lower. The torque multiplier could also be used as a speed tool with a winch as described with reference to Figs. 22 to 26.
  • the use of multiple outputs together with or instead of multiple inputs allows the torque multiplier tool to be used as a step up speed tool.
  • the torque ratio will now be fractional from input to output; however, the speed with be multiplied.
  • the torque multiplier With a tool with ratios of 25:1, 50:1 and 100:1, six different speed/torque ratios can be provided.
  • use of the torque multiplier as a speed tool is particularly effective with multiple stages due to the large differences between ratios.
  • the torque multiplier may also be used as a speed tool with any of the arrangements described in Figs. 1 to 64. Fig.
  • Fig. 69a and 69b illustrate an alternative two-stage torque multiplier.
  • the second stage, indicated as stage 2 in Fig. 69a is functionally similar to the embodiments of torque multipliers previously described.
  • the first stage indicated as stage 1 in fig. 69a has an arrangement of gears as illustrated in Fig. 69b.
  • the first and second stages give a torque multiplication of 5:1 and 4.5:1 respectively.
  • the first and second stages are driven by first and second input drives 690, 692.
  • Rotation of first input drive 690 rotates the first stage and results in a one-stage multiplication of 4.5:1.
  • Rotation of the second input drive 692 rotates the first stage, which, in turn, rotates the second stage and results in a two-stage torque multiplication of 22.5:1 as described above with reference to Fig. 65.
  • Fig. 69b illustrates the arrangement of gears for the first stage of the torque multiplier of Fig. 69a.
  • the first stage gear assembly includes a toothed central sun gear 694, an annular double sided ring gear 696 mounted concentric with the sun gear 694 and which has teeth on both inner and outer sides. This enables transmission of force effectively circumferentially about the first stage of the torque multiplier.
  • a circular outer gear 698 is also provided, which is toothed on its internal side and mounted radially outwardly from the ring gear 696 and is concentric to both the sun gear 694 and the ring gear 696. All the gears are mounted to rotate about a central axis passing through the notional centre of sun gear
  • the first stage gear assembly further includes internal planetary drive gears 695 (located between the central sun gear 694 and the ring gear 696) and external planetary drive gears 697 (located between the double sided ring gear 696 and the circular outer gear 698) .
  • the central sun gear 694 is driven directly by the first input drive 690 or may be indirectly driven by the second input drive 692 acting on the second stage.
  • the central sun gear 694 drives the internal planetary drive gears 695, which in turn drive the double sided ring gear 696.
  • the double sided ring gear 696 drives the external planetary drive gears 697 which, in turn drive the circular output gear 698 at a higher torque than the input torque applied.
  • Fig. 70 shows a further alternative for gearing in a torque multiplier, with three different torque ratios of 1:1, 2.5:1 and 5:1 within a single tool.
  • Fig. 71 shows a two stage torque multiplier including single direction friction drives to give a torque multiplication of 7:1 or 49:1 depending on whether the central torque input 530 or gear torque input 540 is used.
  • Fig. 72a illustrates a torque multiplier generally designated 700 which is generally in the form of a spanner. The tool has an output gear 702 in a portion corresponding to the spanner head.
  • the output gear includes a hexagonal cavity for attachment direct to a nut or other suitable fastener and a square drive cavity 704 for attachment to a square drive so that it can be driven by, or used to drive, a wide range of tools and fasteners.
  • the torque multiplier includes first and second input gears 706, 708.
  • the second input gear 708 is connected to the output gear 702 by an idler gear 711.
  • the first input gear is connected via three idler gears 712, 713, 714 to the second idler gear.
  • a number of screws 715 are illustrated which hold together the casing of the torque multiplier.
  • the first and second input gears 706, 708 are of different diameters (and have different numbers of teeth) and both are considerably smaller (and with fewer teeth) than the output gear 702.
  • the input gears 706, 708 each have a respective square drive cavity 709, 710. It will be appreciated that the number of idler gears is provided so that a clockwise rotation of the input gear 706, 708 results in a clockwise rotation of the output gear 702. It will further be appreciated that due to the size and numbers of teeth of the gears, a torque multiplication is provided.
  • Fig. 72d illustrates an alternative embodiment of a torque multiplier in the general form of a spanner, having an extra pair of gears between the input and output gears to that shown in Fig. 72a, and can receive a torque multiplier of the type discussed above and shown in Fig. 72e.
  • the output gear may be provided with a hexagonal cross-sectional cavity and a suitable adaptor having an external hexagonal shape and a square bore therethrough so as to act as an adaptor between the hexagonal drive output gear and a square drive system.
  • An extension handle may be attached to the torque multiplier via a socket 730. The extension handle can be used to hinder rotation of the torque multiplier during use.
  • Figs. 73a, 73b and 73c show three possible extension handles that may be used. Each has an engaging portion 735 that is insertable to engage with the socket 730.
  • the engaging portions 735 shown in Figs. 73a and 73c are mounted on pivoting ends 740 by axles 745, to allow the handle to extend away from the torque multiplier at various angles.
  • extension handle shown in Fig. 73a includes further sockets 750, 755, which can receive an engaging portion from a further extension handle, so as to provide additional leverage.
  • the extension handles discussed in relation to Fig 73 may be used with any of the above described embodiments having one or more sockets for receiving grounding, extension or bracing members.
  • Fig. 74 illustrates a locking member for the torque multipliers of Figs. 72 and 73.
  • a cylindrical torque multiplier 720 as described above in relation to any one of Figs 1 to 21, or 27 to 73, is also provided, together with a removable locking member 724, which joins the two torque multipliers 700, 720 against relative rotation.
  • the spanner torque multiplier 700 and cylindrical " torque converter 720 include recesses 725 and 726 that receive the removable locking member 724.
  • the removable locking member 724 is inserted into recesses 725 and 726 in order to stop relative movement of the torque multipliers 700, 720.
  • the removable locking member 724 is applied to prevent the cylindrical torque multiplier 720 from rotating relative to the spanner torque multiplier 700.
  • the removable locking member 724 is held in recesses 725 and 726 by any suitable means such as a ball and spring mechanism or via magnetism.
  • the removable locking member 724 also includes sockets 728, and an extension handle, as described above, can be used to engage with the locking member 724, extending away from the locking member 724, for bracing against rotation of the combined multipliers 700, 720 when a torque is applied.
  • Fig. 75 illustrates an alternative embodiment of a torque multiplier in accordance with an aspect of the present invention.
  • the torque multiplier may operate in the same manner as described above with reference to any of Figs. 1 to 21 or 27 to 73.
  • the torque multiplier 800 includes a drum 810 which houses the internal components of the torque multiplier 800 and a base 820, which seals drum 810.
  • the drum 810 forms a cylinder closed at one end and open at the other.
  • the base 820 is configured to close the open end of the drum 810 to seal the internal mechanisms [not shown] of the torque multiplier 800 in the drum 810.
  • the internal mechanisms may be as described above with reference to any of Figs. 1 to 21 or 27 to 73 and are all mounted within the drum. As the internal mechanisms are all mounted to the same mounting frame (i.e. the drum 810) , relative positioning of the internal mechanisms is accurate and not dependent on relative positions of two separate mounting frames.
  • the base 820 then simply provides a seal for the drum 810, as the internal mechanisms are not mounted on the base.
  • the drum and base arrangement is more clearly shown in Fig. 76, which illustrates an exemplary two-stage torque multiplier similar to those discussed above, in which the internal mechanisms 830 are all mounted within the drum 810.
  • the drum 810 and base 820 may be connected by a thread and screw arrangement, via a weld or another suitable connection to form a seal.
  • the seal between the drum 810 and the base 820 is waterproof.
  • the drum 810 and base 820 may be made of aluminium and the aluminium may be anodized.
  • the torque multiplier 800 of Figs. 75 and 76 further includes inputs 801, 802 and 803, and an output 807 [not shown in Fig. 75] .
  • the inputs 801, 802 and 803 are of different sizes in order to be able to receive different sized drivers or tools. Surrounding the inputs 801, 802 and 803 on the outer edge of the drum 810 are indentations 805.
  • the indentations 805 on the outer edge of the drum 810 aid the user in gripping the torque converter for manual rotation of the torque multiplier 800.
  • the torque converter also includes a socket 806 located adjacent to the outer edge of the drum 810 surrounding inputs 801, 802 and 803.
  • the socket 806 is circular in shape and is adapted to receive a bracing rod [not shown] for bracing against rotation of the torque converter 800 while in use. Alternatively, other shaped sockets may be provided.
  • a circular bracing socket is less expensive to machine during manufacture.
  • further sockets may be included along the outer edge of the drum 810 to allow better leverage depending on which of inputs 801, 802 or 803 are being used.
  • the torque multiplier 800 may also be attached to the apparatus for converting torque as described in Figs. 22 to 26 or 72 and 73.
  • an input torque at input 801 will drive the output 807 at a ratio of 13:1, and will also drive the other two inputs 802, 803, which can also be used as outputs for different torque ratios.
  • Figs. 77a to 77f show a single-stage torque multiplier 7700 according to an embodiment of the invention.
  • Fig. 77a shows a semi- transparent plan view of a generally cylindrical torque multiplier.
  • the torque multiplier 7700 has first second and third input portions 7702, 7704, 7706 arranged along a diameter of the cylinder.
  • Fig. 77b shows an axial cross-section of the cylinder of Fig.
  • the first input portion 7702 drives an input gear 7712, which drives idler gears 7714 and supplementary drive gears 7716.
  • the drive and supplementary drive gears 7712, 7716 drive an output ring gear 7718.
  • This drive arrangement is as described above with reference to, for example, Fig. 28.
  • the third input portion 7706 drives input gear 7720, which drives output gear 7718 directly, as described, for example, with reference to Figs 1-9 above.
  • the second input portion 7704 is connected directly to an output portion (shown as 7728 in Fig. 77c) , which does not change the torque between input and output.
  • Figs. 77c through 77f show different cross-sections marked on Fig. 77a.
  • 77c shows that the cylinder is formed in a similar manner to that described with reference to Figs. 75 and 76 above, in that a drum and base are provided, with all the gear mechanisms mounted on the drum.
  • Fig. 77c shows journaling 7722 of the second input portion 7704 to hold it in place in the cylinder, while allowing it to rotate, as well as base 7724, drum 7726 and output portion 7728.
  • Fig. 77d shows a retaining screw 7730, which connects the drum to the base.
  • Fig. 77e shows journaling 7732 on the first and third input portions 7702, 7706.
  • a generally cylindrical unit is described with an input offset from the cylindrical axis.
  • the brace member serves to hinder rotation of the apparatus when an input torque is provided, and thus may be any shape and configuration as is appropriate for the particular use of the apparatus.
  • the brace member is a bar, which extends, at an angle, to the ground.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Retarders (AREA)
  • Transmission Devices (AREA)
  • Structure Of Transmissions (AREA)

Abstract

Un appareil de conversion de couple permettant, selon une variante, de convertir un couple d'entrée relativement petit en un couple de sortie plus grand. L'appareil comprend une partie d'entrée (11, 12, 13) conçue pour recevoir un couple d'entrée, un engrenage d'entrée (27, 28, 29) relié à la partie d'entrée; un engrenage de sortie (19), et une partie de sortie (16), conçue pour obtenir un couple de sortie, en connexion avec l'engrenage de sortie. L'engrenage d'entrée interagit directement avec l'engrenage de sortie. De multiples parties d'entrée peuvent être ménagées et chaque partie peut provoquer un rapport de couple différent entre l'entrée et la sortie.
PCT/AU2005/000134 2004-02-02 2005-02-02 Appareil de conversion de couple WO2005073122A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP05706218A EP1718557A1 (fr) 2004-02-02 2005-02-02 Appareil de conversion de couple
CA002560541A CA2560541A1 (fr) 2004-02-02 2005-02-02 Appareil de conversion de couple
AU2005209335A AU2005209335A1 (en) 2004-02-02 2005-02-02 Apparatus for converting torque

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU2004900455A AU2004900455A0 (en) 2004-02-02 Torque conversion
AU2004900455 2004-02-02

Publications (1)

Publication Number Publication Date
WO2005073122A1 true WO2005073122A1 (fr) 2005-08-11

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Country Status (7)

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EP (1) EP1718557A1 (fr)
KR (1) KR20070019985A (fr)
AU (1) AU2005209335A1 (fr)
CA (1) CA2560541A1 (fr)
TW (1) TW200531800A (fr)
WO (1) WO2005073122A1 (fr)
ZA (1) ZA200607390B (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006016350A1 (de) * 2006-04-05 2007-10-11 Franz-Josef Handwerker Radkreuz mit integriertem schaltbarem Planetengetriebe
WO2014014707A1 (fr) * 2012-07-20 2014-01-23 Cullison Robert F Multiplicateur de couple et procédé d'utilisation
WO2014176468A1 (fr) * 2013-04-24 2014-10-30 HYTORC Division Unex Corporation Appareil de serrage d'elements d'assemblage filetes
WO2018175877A1 (fr) * 2017-03-24 2018-09-27 Tym Labs L.L.C. Module multiplicateur de couple
CN110076719A (zh) * 2018-01-26 2019-08-02 徐博宁 扭矩输入端与扭矩输出端电气绝缘的连接与扭矩传递装置
US20210229592A1 (en) * 2017-03-03 2021-07-29 Wallyxcr, LLC Dual drive torque load binder and method of use thereof
US11267110B2 (en) 2017-08-02 2022-03-08 Tym Labs L.L.C. Zero distance tool

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TW201309427A (zh) * 2011-08-25 2013-03-01 Zhi-Ming Zhang 棘輪扳手
TWI560029B (en) * 2015-12-31 2016-12-01 Drive type open wrench
TWI632992B (zh) * 2017-09-20 2018-08-21 中國氣動工業股份有限公司 旋轉扭力增強裝置

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FR2387804A1 (fr) * 1977-04-22 1978-11-17 Collet Joseph Dispositif pour le demontage des roues de vehicules automobiles et analogues
FR2394368A1 (fr) * 1977-05-02 1979-01-12 Mathien Wolky Reducteur amovible des attache-roues ou ecrous divers
GB2216832A (en) * 1988-03-19 1989-10-18 Charles Walter Stannett Geared wrench
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WO1999052682A1 (fr) * 1998-04-14 1999-10-21 Dein, Kevin Bras prolongateur pour cles a ergots
US20030197160A1 (en) * 2002-04-23 2003-10-23 Curtis David B. Reduced pull chain drive for roll-up doors

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US3973448A (en) * 1973-05-09 1976-08-10 Michelsen Edwin R Electric hoists
FR2387804A1 (fr) * 1977-04-22 1978-11-17 Collet Joseph Dispositif pour le demontage des roues de vehicules automobiles et analogues
FR2394368A1 (fr) * 1977-05-02 1979-01-12 Mathien Wolky Reducteur amovible des attache-roues ou ecrous divers
GB2216832A (en) * 1988-03-19 1989-10-18 Charles Walter Stannett Geared wrench
US5511443A (en) * 1993-11-26 1996-04-30 Brose Fahrzeugteile Gmbh & Co. Kg Cable window lifter with a driving unit
WO1999052682A1 (fr) * 1998-04-14 1999-10-21 Dein, Kevin Bras prolongateur pour cles a ergots
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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006016350A1 (de) * 2006-04-05 2007-10-11 Franz-Josef Handwerker Radkreuz mit integriertem schaltbarem Planetengetriebe
WO2014014707A1 (fr) * 2012-07-20 2014-01-23 Cullison Robert F Multiplicateur de couple et procédé d'utilisation
US9138876B2 (en) 2012-07-20 2015-09-22 Robert F. Cullison Torque multiplier and method of use
WO2014176468A1 (fr) * 2013-04-24 2014-10-30 HYTORC Division Unex Corporation Appareil de serrage d'elements d'assemblage filetes
CN105283272A (zh) * 2013-04-24 2016-01-27 凯特克分部尤尼克斯公司 用于拧紧螺纹紧固件的设备
JP2016516604A (ja) * 2013-04-24 2016-06-09 ハイトーク ディビジョン ユネックス コーポレイション ねじ山付きファスナを締め付ける装置
US20210229592A1 (en) * 2017-03-03 2021-07-29 Wallyxcr, LLC Dual drive torque load binder and method of use thereof
US11691559B2 (en) 2017-03-03 2023-07-04 Wallyxcr, LLC Method of raising or lowering a landing gear
WO2018175877A1 (fr) * 2017-03-24 2018-09-27 Tym Labs L.L.C. Module multiplicateur de couple
GB2575955A (en) * 2017-03-24 2020-01-29 Tym Labs L L C Torque multiplier module
US10427276B2 (en) 2017-03-24 2019-10-01 Tym Labs L.L.C. Torque multiplier module
US11267110B2 (en) 2017-08-02 2022-03-08 Tym Labs L.L.C. Zero distance tool
CN110076719A (zh) * 2018-01-26 2019-08-02 徐博宁 扭矩输入端与扭矩输出端电气绝缘的连接与扭矩传递装置

Also Published As

Publication number Publication date
ZA200607390B (en) 2008-05-28
AU2005209335A1 (en) 2005-08-11
KR20070019985A (ko) 2007-02-16
CA2560541A1 (fr) 2006-09-20
EP1718557A1 (fr) 2006-11-08
TW200531800A (en) 2005-10-01

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