Clutch having abutment surfaces

Abstract

A clutch for lifting a concrete component, including a toroidal connector, a latch movable relative to the toroidal connector between a disengaged condition and an engaged condition, and a coupler for coupling the toroidal connector to a lifting apparatus, wherein the toroidal connector has a circular seat for sitting upon a circular upper surface of a head of and anchor coupled to the toroidal connector, wherein the circular seat terminates in a radial bearing surface for abutment with a castellation of the anchor.

Claims

1. A clutch for lifting a concrete component having an edge-lift eye anchor embedded therein, the clutch comprising: a toroidal connector that defines: an inner circular passage from a front to a rear of the toroidal connector, a lower gap, and an upper opening from a left side to a right side of the toroidal connector; a latch that extends through the inner circular passage and is movable relative to the toroidal connector from: a disengaged condition in which the latch is retracted into the inner circular passage so that the lower gap is open to receive a head of the edge-lift eye anchor, to an engaged condition in which the latch spans the lower gap from the front to the rear of the toroidal connector to pass through an eye of the head and secure the edge-lift eye anchor to the toroidal connector; and a coupler that includes: a lower part that forms a lower loop extending through the upper opening of the toroidal connector, and an upper part, pivotal relative to the lower part, that forms an upper loop configured to couple the toroidal connector to a lifting apparatus, wherein the toroidal connector includes: a left flat bearing surface having a length that spans the lower gap and a width between a left outer edge and a left inner edge that is below the left outer edge; a right flat bearing surface having a length that spans the lower gap and a width between a right outer edge and a right inner edge that is below the right outer edge; a circular seat having a length that spans the lower gap and a width between the left inner edge and the right inner edge; a front inner surface; and a rear inner surface, wherein: the circular seat is arched over the lower gap from the left inner edge to the right inner edge, the left flat bearing surface is angled outwardly in a leftward direction away from a center of the width of the circular seat and is conformed to abut a rightward facing flat surface of a left castellation of the head of the edge-lift eye anchor, the right flat bearing surface is angled outwardly in a rightward direction away from the center of the width of the circular seat and is conformed to abut a leftward facing flat surface of a right castellation of the head of the edge-lift eye anchor, and the circular seat, the left flat bearing surface, the right flat bearing surface, the front inner surface, and the rear inner surface define the lower gap.

2. The clutch of claim 1, wherein the circular seat is circular about an arc having a center at a central longitudinal axis of the latch.

3. The clutch of claim 2, wherein the left flat bearing surface is parallel to a first radius of a circle having a center at the central longitudinal axis of the latch, and the right flat bearing surface is parallel to a second radius of the circle having the center at the central longitudinal axis of the latch.

4. The clutch of claim 1, wherein a plane of the left flat bearing surface and a plane of the right flat bearing surface intersect below the circular seat and below the left and right inner edges.

5. The clutch of claim 1, wherein a plane of the left flat bearing surface and a plane of the right flat bearing surface intersect within the eye of the head when the edge-lift eye anchor is secured to the toroidal connector.

6. The clutch of claim 1, wherein a plane of the left flat bearing surface and a plane of the right flat bearing surface intersect with a portion of the latch that spans the lower gap when the latch is in the engaged condition.

7. The clutch of claim 1, wherein the left flat bearing surface and the right flat bearing surface are angled outwardly to limit rotation of the toroidal connector about the central longitudinal axis of the latch to a predetermined range of rotation by a face-to-face abutment of the left flat bearing surface with the rightward facing flat surface of the left castellation of the head of the edge-lift eye anchor and a face-to-face abutment of the right flat bearing surface with the leftward facing flat surface of the right castellation of the head of the edge-lift eye anchor when the edge-lift eye anchor is secured to the toroidal connector.

8. The clutch of claim 1, wherein the left flat bearing surface is angled outwardly towards the left castellation and the right flat bearing surface is angled outwardly towards the right castellation.

9. A clutch for lifting a concrete component having an edge-lift eye anchor embedded therein, the clutch comprising: a toroidal connector that defines: an inner circular passage from a front to a rear of the toroidal connector, a lower gap, and an upper opening from a left side to a right side of the toroidal connector; a latch that extends through the inner circular passage and is movable relative to the toroidal connector from: a disengaged condition in which the latch is retracted into the inner circular passage so that the lower gap is open to receive a head of the edge-lift eye anchor, to an engaged condition in which the latch spans the lower gap from the front to the rear of the toroidal connector to pass through an eye of the head and secure the edge-lift eye anchor to the toroidal connector; and a coupler that includes: a lower part that forms a lower loop extending through the upper opening of the toroidal connector, and an upper part, pivotal relative to the lower part, that forms an upper loop configured to couple the toroidal connector to a lifting apparatus, wherein the toroidal connector includes: a left sidewall; a right sidewall; a left flat bearing surface having a length that spans the lower gap and a width that extends from a left outer edge at the left sidewall to a left inner edge that is below the left outer edge; a right flat bearing surface having a length that spans the lower gap and a width that extends from a right outer edge at the right sidewall and a right inner edge that is below the right outer edge; a circular seat having a length that spans the lower gap and a width between the left inner edge and the right inner edge; a front inner surface; and a rear inner surface, wherein: the circular seat is arched over the lower gap from the left inner edge to the right inner edge, the left flat bearing surface is angled outwardly in a leftward direction away from a center of the width of the circular seat and is conformed to abut a rightward facing flat surface of a left castellation of the head of the edge-lift eye anchor; the right flat bearing surface is angled outwardly in a rightward direction away from the center of the width of the circular seat and is conformed to abut a leftward facing flat surface of a right castellation of the head of the edge-lift eye anchor, the circular seat, the left flat bearing surface, the right flat bearing surface, the front inner surface, and the rear inner surface define the lower gap, and the left flat bearing surface and the right flat bearing surface are angled outwardly to enable rotation of the toroidal connector about a longitudinal axis of the eye of the head when the edge-lift eye anchor is secured to the toroidal connector.

10. The clutch of claim 9, wherein the left flat bearing surface and the right flat bearing surfaces are angled outwardly to limit the rotation of the toroidal connector about the longitudinal axis of the eye of the head to a predetermined range of rotation when the edge-lift eye anchor is secured to the toroidal connector.

11. The clutch of claim 10, wherein the predetermined range of motion corresponds to a difference between (a) an angular aperture, about the longitudinal axis of the eye of the head, between the left and right castellations of the anchor, and (b) an angular aperture, about the longitudinal axis of the eye of the head, between the left flat bearing surface and the right flat bearing surfaces of the toroidal connector.

12. The clutch of claim 9, wherein a plane of the left flat bearing surface and a plane of the right flat bearing surface intersect below the circular seat and below the left and right inner edges.

13. A clutch for lifting a concrete component having an edge-lift eye anchor embedded therein, the clutch comprising: a toroidal connector that defines: an inner circular passage from a front to a rear of the toroidal connector, a lower gap, and an upper opening from a left side to a right side of the toroidal connector; a latch that extends through the inner circular passage and is movable relative to the toroidal connector from: a disengaged condition in which the latch is retracted into the inner circular passage so that the lower gap is open to receive a head of the edge-lift eye anchor, to an engaged condition in which the latch spans the lower gap from the front to the rear of the toroidal connector to pass through an eye of the head and secure the edge-lift eye anchor to the toroidal connector; and a coupler that includes: a lower part that forms a lower loop extending through the upper opening of the toroidal connector, and an upper part, pivotal relative to the lower part, that forms an upper loop configured to couple the toroidal connector to a lifting apparatus, wherein the toroidal connector includes: a left flat bearing surface having a length that spans the lower gap and a width between a left outer edge and a left inner edge that is below the left outer edge; a right flat bearing surface having a length that spans the lower gap and a width between a right outer edge and a right inner edge that is below the right outer edge; a circular seat having a length that spans the lower gap and a width between the left inner edge and the right inner edge; a front inner surface; a rear inner surface; a left sidewall; and a right sidewall, wherein; the circular seat is arched over the lower gap from the left inner edge to the right inner edge, the left flat bearing surface is angled outwardly in a leftward direction away from a center of the width of the circular seat and is conformed to abut a rightward facing flat surface of a left castellation of the head of the edge-lift eye anchor in a face-to-face abutment when the edge-lift eye anchor is secured to the toroidal connector, the right flat bearing surface is angled outwardly in a rightward direction away from the center of the width of the circular seat and is conformed to abut a leftward facing flat surface of a right castellation of the head of the edge-lift eye anchor in a face-to-face abutment when the edge-lift eye anchor is secured to the toroidal connector, the circular seat, the left flat bearing surface, the right flat bearing surface, the front inner surface, and the rear inner surface define the lower gap.

14. The clutch of claim 13, wherein the left flat bearing surface conforms to the left castellation of the head of the edge-lift eye anchor and the right flat bearing surface conforms to the right castellation of the head of the edge-lift eye anchor.

15. The clutch of claim 13, wherein a plane of the left flat bearing surface and a plane of the right flat bearing surface intersect below the circular seat and below the left and right inner edges.

16. The clutch of claim 13, wherein a plane of the left flat bearing surface and a plane of the right flat bearing surface intersect within the eye of the head when the edge-lift eye anchor is secured to the toroidal connector.

17. The clutch of claim 13, wherein a plane of the left flat bearing surface and a plane of the right flat bearing surface intersect within region of the lower gap of the toroidal connector that is spanned by the latch in the engaged condition.

18. The clutch of claim 13, wherein the left flat bearing surface and the right flat bearing surface are angled outwardly to limit the rotation of the toroidal connector about the central longitudinal axis of the latch to a predetermined range of rotation by the face-to-face abutments.

19. The clutch of claim 13, wherein an intersection of a plane of the left flat bearing surface and a plane of the right flat bearing surface spans the lower gap within a portion of the latch that spans the lower gap when the latch is in the engaged condition.

20. The clutch of claim 13, wherein the left flat bearing surface and the right flat bearing surface are angled outwardly to enable rotation of the toroidal connector about a longitudinal axis of the eye of the head.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The present disclosure is further described by way of non-limiting example only with reference to the accompanying drawings, in which:

(2) FIG. 1 shows a perspective view of an articulated clutch for lifting a concrete component in accordance with an example of the present disclosure;

(3) FIG. 2 shows a side view of the articulated clutch;

(4) FIG. 3 shows a front view of the articulated clutch;

(5) FIG. 4 shows an exploded view of the articulated clutch;

(6) FIG. 5 shows a front view of the articulated clutch, depicting a tamper evident device incorporated into the clutch;

(7) FIG. 6 shows a side cross-sectional view of the articulated clutch, depicting location of the tamper evident device when in situ;

(8) FIG. 7 is a detailed perspective view of an end of the tamper evident device when in situ;

(9) FIG. 8 shows a perspective view of the articulated clutch, depicting a limit of rotation of a second part of a coupler relative to a first part of the coupler;

(10) FIG. 9a shows a front view of the articulated clutch, depicting the limit of rotation of the second part relative to the first part;

(11) FIG. 9b shows a cross-sectional view of the articulated clutch taken along line A-A shown in FIG. 9a;

(12) FIG. 9c shows a side view of the articulated clutch, depicting the limit of rotation of the second part relative to the first part;

(13) FIG. 10 shows a side perspective view of a toroidal connector of the articulated clutch;

(14) FIG. 11a shows a front view of the toroidal connector;

(15) FIG. 11b shows a side cross-sectional view of the toroidal connector taken along line A-A shown in FIG. 11a;

(16) FIG. 12 shows an opposite side perspective view of the toroidal connector;

(17) FIG. 13 shows a cross-sectional view of the toroidal connector when connected to a head of a cast-in anchor, taken through a central plane of the toroidal connector;

(18) FIG. 14 shows a front view of a coupler of the articulated clutch, depicting an axis of rotation of the second part relative to the first part with respect to a central line of the coupler connecting a centre of a circular arc of the first part with a centre of a circular arc of the second part;

(19) FIG. 15 shows a side view of an articulated clutch in accordance with another example, depicting the limit of rotation of the coupler relative to the toroidal connector;

(20) FIG. 16 shows a perspective view an articulated clutch in accordance with another example, depicting a locking ring handle being sufficiently long to limit rotation of the coupler relative to the toroidal connector;

(21) FIG. 17 shows a top view of the articulated clutch shown in FIG. 16;

(22) FIG. 18 shows a side view of the articulated clutch shown in FIG. 16;

(23) FIG. 19 shows a perspective view of the articulated clutch in accordance with another example;

(24) FIG. 20 shows a detailed view of portion labelled B in FIG. 19;

(25) FIG. 21 shows a front view of the articulated clutch shown in FIG. 19 and FIG. 20; and

(26) FIG. 22 shows a detailed view of section A-A shown in FIG. 21.

DETAILED DESCRIPTION

(27) As can be seen in FIGS. 1 to 18 of the drawings, the present disclosure may provide an articulated clutch for lifting a concrete component. Advantageously, the articulated clutch has a coupler including a first part and a second part pivotal relative to the first part. The first part forms a first loop and the second part forms a second loop. The two loops are dissimilar in size such that the top loop (when lifting) provided by the second loop will accept a crane or lifting hook but can still accept a suitable size chain fitted directly to the top loop.

(28) More specifically, as shown in FIGS. 1 to 4, there is provided a clutch 10 for lifting a concrete component (not shown). The concrete component may take several forms including, but not limited to, a concrete panel. The concrete component may have a cast in edge lift anchor (for example), the anchor having an eye which is used for connection to a toroidal connector of the clutch 10 for lifting the concrete panel.

(29) The clutch 10 includes a toroidal connector 12 and a latch 14. The latch 14 is movable relative to the toroidal connector 12 between a disengaged condition (in which the latch 14 is retracted into a toroidal sleeve of the toroidal connector 12) and an engaged condition (see FIG. 2) in which the latch 14 spans a gap of the toroidal connector 12 for engagement with an eye of and anchor cast into a concrete component. The clutch 10 also includes a coupler 16 for coupling the toroidal connector 12 to a lifting apparatus 18, wherein the coupler 16 is articulated.

(30) The coupler 16 includes a first part 20 and a second part 22 pivotal relative to the first part, the first part forming a first loop 24 engaged through the toroidal connector 12 and the second part 22 forming a second loop 26 for receiving the lifting apparatus 18.

(31) As shown, the first loop 24 is a different size to the second loop 26. More specifically, the first loop 24 is smaller than the second loop 26. The second loop 26 is adapted to allow direct fitment of a lifting chain while also allowing direct fitment of a lifting hook. Accordingly, the coupler 16 allows the direct fitment of a suitable size chain like a hammerlock but also allows for direct fitment to a lifting hook as shown in FIG. 5.

(32) The articulation of this format of clutch handle (in the form of coupler 16) addresses the issue of welded handles getting bent around the head of a concrete panel as the panel is lifted off a truck at a building site, as the concrete panel is lifted and then rotated 90 before being positioned. It does this while also meeting the needs of the precast factory where the clutch 10 is used to lift concrete panels from horizontal to vertical after casting and for moving them to curing racks and later onto trucks for transportation to a building site.

(33) The compact size of the two loops (the first loop 24 and the second loop 26) also allows for greater head height within the factory, allowing for a gain in lifting height. This in turn allows for increased panel sizes as well as increased manoeuvrability within the factory, where lifting height is limited by the gantry height.

(34) As shown in FIG. 4, the coupler 16 includes an elongated axle pin 28 about a longitudinal axis of which the second part 22 is pivotal relative to the first part 20. The first part 20 includes a forked end and a non-forked end. The forked end of the first part 20 engages with a non-forked end of the second part 22, whereas the non-forked end of the first part 20 engages with a forked end of the second part 22. The ends of the first part 20 and the second part 22 are provided with apertures through which the axle pin 28 is passed so as to hold together in pivotal relationship the first part 20 and the second part 22.

(35) With reference to FIG. 4, the latch 14 is in the form of a circular latch passing through an inner circular passage of the toroidal connector 12. The latch 14 has a handle 30 for moving the latch 14 between the disengaged condition and the engaged condition, the handle 30 extending generally radially outwardly relative to a centre of the toroidal connector 12.

(36) As shown most clearly in FIG. 14, the first part 20 has a first circular arc 32 and the second part 22 has a second circular arc 34. The pin 28 is located such that a longitudinal axis of the pin 28 is perpendicular to a line 36 connecting a centre 38 of the first arc 32 to a centre 40 of the second arc 34.

(37) Accordingly, the axle pin 28 runs perpendicular to the centre line between the arcs of the two loops 24, 26. This allows the handle (coupler 16) to be symmetrical such that when rotated about the toroidal connector 12, the coupler 16 has the same angular movement either way. This perpendicular configuration may also assist in the articulation of the coupler 16 when it needs to be bent around the end of a concrete panel being lifted.

(38) Turning to FIGS. 8 to 9c, the latch 14 in the form of the locking ring may have a handle 30 extending generally radially outwardly from the toroidal connector 12. The coupler 16 may be specifically arranged to limit pivotal movement of the second part 22 relative to the first part 20. In other words, in FIG. 2 the first part 20 and the second part 22 are shown in a co-planar configuration, whereas in FIGS. 8 to 9c there is shown a limit of pivotal movement of the second part 22 relative to the first part 20.

(39) In one form, the coupler 16 may be arranged to limit pivotal movement of the second part 22 relative to the first part 20 in one direction. The coupler 16 may also be arranged to limit pivotal movement of the second part 22 relative to the first part 20 such that the limit prevents a tip 42 of the locking ring handle passing through an inner loop 26 of the second part 22.

(40) As best shown in the cross-sectional drawing shown in FIG. 9B, the first part may include a shoulder 44 arranged to bear against the second part 22 at the limit. Alternatively, or in addition, the second part 22 may include a shoulder arranged to bear against the first part 20 at the limit.

(41) In a preferred example, the coupler 16 is arranged to limit pivotal movement of the second part 22 relative to the first part 20 such that the limit prevents the second part 22 from engaging with the locking ring handle 30 to rotate the locking ring handle 30. More specifically, the coupler 16 may be arranged to limit pivotal movement of the second part 22 relative to the first part 20 such that the limit prevents the second part 22 from engaging with the locking ring handle 30 to rotate the locking ring handle 30 from the engaged condition to the disengaged condition.

(42) In this way, the two loops 24, 26 are limited in rotation in one direction to eliminate the large loop being able to hook under the locking ring handle 30. The applicant has identified that, where the upper loop (secondly 26) is large enough to accept a lifting hook, then that loop has the potential to cook under the locking ring handle 30 and could allow the clutch 10 to become disconnected from the anchor unintentionally. Advantageously, by limiting rotation in this way examples of the present disclosure are able to prevent unintentional disconnection.

(43) As shown in FIGS. 4 to 7, the second part 22 is pivotal relative to the first part 20 about the axle pin 28. The coupler 16 may also include a tamper evident indicator 46 to indicate that the clutch 10 has not been disassembled. The tamper evident indicator may be is arranged to indicate that the axle pin 28 has not been removed from the coupler 16. In the example shown, the coupler 16 is provided with a bush 48 around a central portion of the axle pin 28, the central portion being between the distal end of the first part 20 and the second part 22. The second part 22 may be provided with longitudinal slots which are received in corresponding longitudinal grooves of the bush 48 to keep the bush 48 aligned relative to the second part 22 and to prevent rotation of the bush 48 relative to the second part 22.

(44) With reference to FIG. 4, the pin 28 may have a circular groove 50 about its circumference and the tamper evident indicator 46 may include a member in engagement with the circular groove 50 to prevent movement of the pin 28 along its longitudinal axis relative to the bush 48. In addition, the toroidal connector 12 may be provided with a stop pin 52 to limit rotation of the latch 14 relative to the toroidal connector 12. The member 46 may be anchored to the bush 48. With reference to FIG. 6, the member 46 may be in the form of a rivet which passes through the bush 48 and has a flange at each end to retain the rivet relative to the bush 48. Alternatively, the member may be in the form of a roll pin.

(45) In this way, there is provided a tamper evident centre bush 48. The bush 48 may be profiled to match the loops 24, 26, the bush 48 being secured by either a rivet or a roll pin that does not pass through the middle of the axle pin 28 but passes tangentially through the groove 50 on the axle pin 28. If secured by a rivet, the rivet will be deformed to secure it and the deformed end may have a branded logo (see FIG. 5 and FIG. 7) to indicate the handle (coupler 16) has not been tampered with. If a roll pin is used, then a seal (possibly in the form of epoxy or solder) may be used to indicate the clutch 10 has not been disassembled.

(46) As will be appreciated from the drawings, the bush 48 has a non-cylindrical shape. The locking pin or rivet 46 runs tangentially through the groove 50 in the axle pin 28. Accordingly, this provides an indication to the user that the clutch 10 has not been tampered with since proof testing. The applicant has identified that a commercial hammerlock can be disassembled and reassembled without it being evident that this has happened. Therefore, the original proof testing and certification could be invalid as this must be conducted anytime the clutch is modified.

(47) Advantageously, the incorporation of a tamper evident feature gives the user confidence that the clutch 10 has not been tampered with since proof testing. The unique shape of the bush 48 allows the rivet or cross pin 46 to hold the axle 28 by the groove 50 rather than passing the centre of the axle 28. This creates far less stress concentration, making the axle 28 stronger. The unique shape of the bush 48 also allows the use of the tamper evident rivet 46. The tangentially positioned groove 50 allows for easier assembly of the system compared to that of a centrally located hole as less alignment is required (that is, alignment is only required in the x-axis and not in both x and y axes).

(48) Turning now to FIGS. 10 to 13, the toroidal connector 12 may be provided with a circular seat 54 for sitting upon a circular upper surface 56 of a head 58 of an anchor 60 coupled to the toroidal connector 12. The circular seat 54 terminates in a radial bearing surface 62 for face-to-face abutment with a castellation 64 of the anchor 60.

(49) As can be seen most clearly in FIG. 13, the circular seat 54 has a first radial bearing surface 62 for abutment with a first castellation 64 of the anchor and a second, opposite, radial bearing surface 62 for abutment with a second castellation 64 of the anchor 60.

(50) In the example shown, the circular seat 54 is circular about an arc 66 having a centre at a central longitudinal (tangential) axis 68 of the latch 14. More specifically, the radial bearing surface 62 is radial relative to a circle having a centre at the central longitudinal axis 68 of the latch 14.

(51) Advantageously, the provision of the radial bearing surfaces 62 improve the interface of the toroidal connector 12 and the anchor 60, when compared with existing connectors which abut at an edge or point. The applicant has identified that the face-to-face bearing provides less pressure owing to the greater surface area of contact, reducing wear on the toroidal connector 12. In particular, the applicant has identified that previous clutch designs for castellated anchors would see the sides of the torus bear on the castellations (or in a point or line contact where the sides of the torus meet the curved cut out). In the example of the present disclosure shown, a new angled face interacts with the angled face of the anchor 60 to achieve a far greater bearing area resulting in less wear on the torus over time. This is achieved by way of the angled faces on the toroidal connector 12 which bear against the castellations 64 on the head 58 of the anchor 60. This is in contrast to existing arrangements where a toroidal connector bears on flat faces of the anchor or, where the anchor is castellated, the sides of the torus bear on the castellations.

(52) With reference to FIGS. 15 to 18, there is shown an alternative example of the present disclosure in which the locking ring handle 30 is arranged to abut the coupler 16 to limit rotational movement of the coupler 16 relative to the toroidal connector 12. In particular, the locking ring handle 30 is arranged to limit rotational movement of the coupler 16 relative to the toroidal connector 12 such that the limit prevents a tip 42 of the locking ring handle 30 passing through an inner loop 26 of the coupler 16. This may be achieved by dimensioning the locking ring handle 30 such that the tip 42 of the locking ring handle 30 extends radially further from a centre of the toroidal connector 12 than an outermost edge of the coupler 16.

(53) Turning to FIGS. 19 to 22, there is shown an example of the present disclosure in which the coupler 16 is arranged to limit pivotal movement of the second part 22 relative to the first part 20 in two directions. More specifically, as can be seen in FIG. 19, the first part 20 is connected to the second part 22 by a pivotal coupling 70. In the example shown, the pivotal coupling 70 includes a first hinge 72 at one side of the coupler 16 and a second hinge 74 at an opposite side of the coupler 16. As can be seen, the first hinge 72 and the second hinge 74 are arranged to provide pivotal movement of the second part 22 relative to the first part 21 along a common axis which may be ensured by a single axle pin 28.

(54) In the example shown in FIGS. 19 to 22, the pivotal coupling 70 includes a bush 48 between the first hinge 72 and the second hinge 74. The bush 48 includes a stop 76 for abutting against the first part 20 or the second part 22 to limit rotation of the second part 22 relative to the first part 20. The bush 48 may be arranged to rotate with the second part 22 (for example, engaged with the second part 22 by way of a tongue and groove connection) and the stop 76 may be adapted to abut against the first part 20 to limit rotation of the second part 22 relative to the first part 20.

(55) FIG. 20 shows an enlarged and detailed view of the portion labelled B in FIG. 19. In FIG. 20 it can be seen that the first part 20 is provided with a tab 78 for abutment with the stop 76.

(56) FIG. 21 shows a front view of the coupler 16, and FIG. 22 shows an enlarged and detailed view of the cross-section labelled A-A in FIG. 21. With reference to FIG. 22, the stop 76 may be in the form of a cutout 80 having two stop surfaces, comprising a first stop surface 82 for abutting one side of the tab 78 and a second stop surface 84 for abutting an opposite side of the tab for limiting rotation of the second part 22 relative to the first part 20 in two directions.

(57) Advantageously, this arrangement enables the limiting of angular movement of the second part 22 relative to the first part 20 in two directions and avoids a weakness which may otherwise be incurred if the limiting mechanism is attempted to be achieved within the first hinge 72 and/or the second hinge 74. The arrangement shown in FIGS. 19 to 22 takes advantage of there being no load or only little load on the coupler 16 when the rotation limiting mechanism is required to perform its duty. In other words, the arrangement shown in FIGS. 19 to 22 changes how rotation of the upper loop relative to the lower loop is achieved. In this revised version, this limitation of rotation is achieved between radial shoulders in the centre bush 48 that limit the movement of a lug or tab on the inside of the lower loop.

(58) The revised arrangement limits rotation in both directions, not just one direction. It will be understood by those skilled in the art that the two directions may be different (for example, in magnitude of limitation), thereby preventing the large loopthe second partfrom interacting with the locking ring handle while allowing extra rotation in the opposite direction. This revised arrangement works between the lower loopthe first part 20and the centre bush 48, where the centre bush 48 is keyed to the upper bush to maintain alignment with the upper loop.

(59) While various embodiments of the present disclosure have been described above, it should be understood that they have been presented by way of example only, and not by way of limitation. It will be apparent to a person skilled in the relevant art that various changes in form and detail can be made therein without departing from the spirit and scope of the present disclosure. Thus, the present disclosure should not be limited by any of the above described exemplary embodiments.

(60) The reference in this specification to any prior publication (or information derived from it), or to any matter which is known, is not, and should not be taken as an acknowledgment or admission or any form of suggestion that that prior publication (or information derived from it) or known matter forms part of the common general knowledge in the field of endeavour to which this specification relates.

LIST OF FEATURES

(61) 10 Clutch 12 Toroidal connector 14 Latch 16 Coupler 18 Lifting apparatus 20 First part 22 Second part 24 First loop 26 Second loop 28 Axle pin 30 Handle of the latch 32 First circular arc 34 Second circular arc 36 Line 38 Centre of the first arc 40 Centre of the second arc 42 Tip of the locking ring handle 44 Shoulder 46 Tamper evident indicator 48 Bush 50 Circular groove 52 Stop pin 54 Circular seat 56 Circular upper surface 58 Head 60 Anchor 62 Radial bearing surface 64 Castellation 66 Arc 68 Central longitudinal axis of the latch 70 Pivotal coupling 72 First hinge 74 Second hinge 76 Stop 78 Tab 80 Cutout 82 First stop surface 84 Second stop surface