Patent Application
20130328328
1. Technical Field
The present invention relates to a compression latch for a closure.
2. Related Art
It is known to use compression latches in a variety of applications, for example when force is required to hold a closure in place, or when sealing of a closure (e.g. a door, window or access panel of a vehicle or an item of construction plant) is needed. Compression latches often incorporate a pivoting latch arm held against a closure surround by latch mechanism, and biased into an open position by a spring or other resiliently biased device. The latch mechanism holds the latch arm in a closed position so that pressure is applied by the latch to a closure to keep it shut and/or seal it. Upon release of the latch mechanism, the resilient biasing device causes the latch arm to pivot open enabling the associated closure to be opened. Compression latches are typically mounted in an aperture cut from the sheet metal material of the closure.
There can be difficulties with existing compression latches of this type. The latch arm must clear the closure surround when the latch is in a fully open position, so that it does not prevent the closure from being fully opened. Considerable force may be required to close a latch, particularly where the latch is required to seal a closure. It is known to increase the length of the lever handle to allow a greater amount of mechanical advantage to be applied to the latch arm whilst limiting the force required at the handle, but this leads to increased space requirement, and for a requirement for a larger aperture to be cut in the closure. In addition, the level of mechanical advantage is fixed throughout the range of motion of the lever.
Where the closure is relatively large, it may be desirable for additional “satellite” compression latches to be connected to the main latch, and operated from it, in order to provide optimal retention. One way in which this may be achieved is to utilize the pivot point of the main latch as a “power take-off” for shafts to connect the satellite latches. However, the location of this pivot point on known latches is too close to the face of the closure for the shafts to be able to rotate freely.
A disadvantage of such satellite latches is the difficulty of providing compression at the satellite latch point. Applying compression at the satellite latch can lead to a shaft connecting a main latch and a satellite latch being subjected to unwanted torsion, which can weaken the shaft and reduce the compression applied.
A known latch of this type is disclosed in GB2264530 (Southco). It is not possible to alter the relative motion of the handle and the latch arm of the latch disclosed in GB2264530. The only way to vary the mechanical advantage of that latch is to vary the length of the handle and the latch arm. In addition, the pivot point is too close to the closure face to act as a power take-off.
The present invention seeks to overcome, or at least mitigate, the problems of the prior art.
According to the present invention there is provided a compression latch for a closure, comprising a housing, a handle and a latch member having a first end and a second end; wherein the housing has an inboard side and an outboard side, and defines a plane substantially parallel to a plane of said closure; the handle is pivotably connected to the housing at a handle pivot point, the handle pivot point having a longitudinal axis substantially parallel to said plane; the latch member first end is pivotably connected to the housing through a latch member pivot point remote from the handle pivot point and inboard thereof, the latch member pivot point having a longitudinal axis substantially parallel to the handle pivot point longitudinal axis; the latch member being pivotable about the latch member pivot point between an open position and a closed position; the handle is connected to the latch member by a first linkage such that the latch member is moveable between said open position and said closed position by angular movement of the handle about the handle pivot point; and the latch member comprises a striker at its second end.
The advantage provided by the above compression latch is that, due to separation of the handle and latch member pivot points, the resultant force applied by the latch member at a given region of its motion may be adjusted or tuned for a given input, improving ease of latch closure or for other ends.
The handle pivot point may be on the outboard side of the housing, and/or the latch member pivot point may be on the inboard side of the housing. The inboard side of the housing may comprise a seal configured to seal the inbound side of the housing from the outboard side of the housing. The handle pivot point may include a handle shaft extending between the inboard and outboard sides of the housing, and the first linkage may be connected to the drive shaft.
The first linkage may be configured such that angular movement of the handle about the handle pivot point results in smaller angular movement of the latch member at at least one position throughout its range of motion. The ratio of the angular movement of the handle to that of the latch member may vary depending upon the angular position of the latch member. The latch member may move through at least two zones, including an active zone adjacent the closed position, between the closed position and the open position, and the ratio of the angular movement of the handle may be greater in the active zone compared to outside the active zone. The ratio of the angular movement of the handle to that of the latch member may be between 1.1 and 1.5 when the latch member is within the active zone, and the ratio of the angular movement of the handle to that of the latch member may be between 1.2 and 1.4 when the latch member is within the active zone.
The latch member may be resiliently biased towards the open position, or may be resiliently biased towards the closed position.
The latch member may be pivotably connected to the housing by a second linkage, which may comprise first and second connection members pivotably connected between the latch member and the housing. The first and second connection members may form a parallelogram linkage with the housing and the latch member, and wherein motion of the parallelogram linkage may be controlled by the first linkage.
The first linkage may be at least a four-bar linkage, which may comprise a first link pivotably connected to the handle pivot point, and a second link pivotably connected to the first link at a linkage pivot point and pivotably connected to the latch member at a second link pivot point. The linkage pivot point may be inboard relative to the latch member. The first linkage may use over-centre motion to move between the closed position and an open position.
The handle pivot point may be between the latch member pivot point and the striker in a direction substantially parallel to the plane.
The first linkage may be a four-bar linkage. The linkage pivot point may be outboard relative to the latch member.
Where the latch member is resiliently biased towards the open position, the first linkage may retain the latch member in a lost motion arrangement such that movement of the latch member towards the open position is controlled by the first linkage.
The latch pivot point may be translatable with respect to the housing. The housing may define a guide track along which the latch pivot point is slidable. The guide track may include a dogleg configured to receive the latch pivot point as the closed position is approached.
In certain embodiments, the first linkage may be translatably connected to the latch member, and the shaft member may define a guide track along which an end of the first linkage is slidable, which may be curved. The guide track may include a dogleg configured to receive said end of the first linkage as the closed position is approached.
The handle pivot point may be fixed in relation to the latch member pivot point. The latch member pivot point may be inboard of the handle pivot point, and/or the handle pivot point may be between the latch member pivot point and the striker in a direction substantially parallel to the plane.
There is further provided a compression latch for a closure, comprising a housing, a handle and a latch member having a first end and a second end. The housing has an inboard side and an outboard side, and defines a plane substantially parallel to a plane of said closure. The handle is pivotably connected to the housing at a handle pivot point, the handle pivot point having a longitudinal axis substantially parallel to said plane. The handle is connected to the latch member by a first linkage. The latch member first end is pivotably connected to the housing by a second linkage. The latch member is moveable in relation to the housing between an open position and a closed position; such that the latch member is moveable between said open position and said closed position by angular movement of the handle about the handle pivot point. The latch member comprises a striker at its second end.
The second linkage may comprise first and second connection members pivotably connected between the latch member and the housing. The first and second connection members may form a parallelogram linkage with the housing and the latch member, and motion of the parallelogram linkage may be controlled by the first linkage.
The first linkage may comprise a first link pivotably connected to the handle pivot point, and a second link pivotably connected to the first link at a linkage pivot point and pivotably connected to the latch member at a second link pivot point.
The latch member may be cranked away from the housing when in the closed position. The striker may be adjustable. The compression latch may further comprise a latching mechanism configured to retain the latch when the latch member is in the closed position, and/or may further comprise a lock, and/or a padlock loop. The padlock loop may extend through an aperture defined by the handle therefor. The latch member pivot point may include a non-circular projection configured for the attachment of an extension shaft arranged to rotate with the latch member.
There may further be provided a compression latch assembly incorporating a compression latch as described above, which may further comprise at least one additional latch member pivotable about a fifth pivot point remote to the latch member pivot point, configured such that the at least one additional latch member is actuated by movement of the latch member of the compression latch.
There is yet further provided a compression latch for a closure comprising a latch mount having an inboard side and an outboard side and a latch member having a first end and a second end; and a drive shaft configured to drive the compression latch, wherein the shaft is actuated remotely. The drive shaft is pivotably connected to the mount at a first link pivot point, the first link pivot point having a first longitudinal axis. The latch member first end is pivotably connected to the mount at a latch member pivot point remote from the first link pivot point and inboard thereof, the latch member pivot point having a second longitudinal axis substantially parallel to the first longitudinal axis; the latch member being pivotable about the latch member pivot point between an open position and a closed position. The latch member is connected to the drive shaft by a linkage such that the latch member is moveable between said open position and said closed position by rotation of the drive shaft. The latch member comprises a striker at its second end.
The latch member pivot point being remote from the first link pivot point provides a difference in angular movement of the latch member and the drive shaft that causes the force provided by the latch member to be increased as the closed position is neared. This advantageously provides a compressive force on the closure from the secondary latch.
The linkage may be configured such that angular movement of the drive shaft results in smaller angular movement of the latch member at at least one position throughout its range of motion.
The ratio of the angular movement of the drive shaft to that of the latch member may vary depending upon the angular position of the latch member.
The latch member may move through at least two zones, including an active zone adjacent the closed position, between the closed position and the open position, and the ratio of the angular movement of the drive shaft to that of the latch member may be greater in the active zone compared to outside the active zone.
The linkage may be at least a four-bar linkage.
The linkage may comprise a first link pivotably connected to the first link pivot point and a second link pivotably connected to the first link at a linkage pivot point and pivotably connected to the latch member at a second link pivot point.
The linkage may use over-centre motion to move the latch member between the closed position and the open position. The second link may be configured to be pivoted by the first link with respect to the latch member so as to provide over-centre motion.
The mount may define a recess configured to receive the linkage pivot point. The recess may be configured to receive the linkage pivot point when the latch member is substantially in the closed position.
The first link may be a single piece of sheet metal.
The second link may be a rod. The second link may extend at least partially through the first link to form the linkage pivot point, and/or may extend at least partially through the latch member to form the second link pivot point.
The latch member may be a single piece of sheet metal. The mount may be a single piece of sheet metal.
The striker may be adjustable.
The latch may be configured for use as a secondary compression latch in an assembly having a primary compression latch.
There is also provided a latch assembly for a closure comprising a primary compression latch comprising a latch member configured for pivotable movement between an open position and a closed position; at least one latch according to any preceding claim as a secondary compression latch; and a connection arrangement connecting the primary compression latch and the drive shaft. The drive shaft is actuated by the primary compression latch.
The drive shaft may be actuated by the latch member of the primary compression latch. The latch member of the secondary latch may reach the closed position after the latch member of the primary latch reaches the closed position.
The latch member of the secondary latch may be at an angle to, or perpendicular to, the latch member of the primary latch, and the assembly may further comprise a connection arrangement between the secondary latch and the primary latch to actuate movement of the latch member of the secondary latch at an angle to the latch member of the primary latch.
A compression latch will now be described in detail by way of example and with reference to the accompanying drawings in which:
a is a perspective view of a latch according to the embodiment of
b is a perspective view of the latch of
Referring to
The housing 12 defines an outboard side 19 and an inboard side 20, and includes a main body 18. The housing has a first edge 7 intended to be mounted proximal a free edge of a closure 9 (i.e. the edge over which the latch member extends). The inboard side 20 is substantially sealed from the outboard side 19 to inhibit the ingress of water through the latch 10.
The housing body 18 has at its inboard side a peripheral channel configured to receive a gasket (not shown), allowing the housing 12 to be sealed against the closure 9. When installed in the closure 9 the housing 12 is held in place by a bracket 11. The channel defines a housing body plane coincident with the plane of the closure in which the latch 10 is installed.
The housing 12 has in its outboard side 19 a shallow recess 15, and a handle recess 21 off the recess 15, with walls 22 extending inboard 20, substantially normal to the plane. The recesses 15, 21 are configured to receive the handle 16 when the latch 10 is in a closed position. The shallow recess 15 is generally oval shaped and has space to allow the handle 16 to be grasped easily when the latch 10 is in the closed position.
The walls 22 define a pivot mounting point 23 for the handle 16 in the form of two co-axial circular apertures (not shown) in the side walls 22. The inboard side 20 of the housing 12 includes a latch member mounting point 26 in the form of circular apertures in two parallel protrusions 28 extending inboard of the housing 12.
In this embodiment the housing 12 is of 30% glass-filled nylon. Alternative materials may be used, for example other injection-moulded plastics or injection-moulded metal.
The handle 16 has a handle arm 44 having a free end 46 and a connection end 48. The free end 46 is in this embodiment substantially T-shaped, having a curved bar 50 perpendicular to the remainder of the arm 44 for ease of use. The handle arm 44 defines a padlock loop aperture 52 through which a padlock loop 25 extending outboard from the handle recess 21 extends when the handle 16 is in the closed position, allowing a padlock (not shown) to be clipped through the loop 52. The handle connection end 48 defines a bore (not shown).
The handle 16 is pivotably connected to the outboard side 19 of the housing 12 by a handle shaft 54 (see
The handle shaft 54 is cylindrical for most of its length and has semi-circular ends 58 with a flat face 59 (see
In alternative embodiments, the spring 60 may be arranged to return the handle 16 to the closed position.
The housing 12 also has at its outboard side 19 a cylindrical lock recess 29, which houses a cylinder lock 24. The lock 24 includes a latching mechanism 24a used to retain the latch 10 when in the closed position, and prevents unauthorised release of the latching mechanism 24a. The lock 24 includes a push-button latch release mechanism (not shown) and a pivotable cover flap 37.
The latch member 14 has a latch arm 30 having a striker end 32 and a connection end 34, and a striker 36 in the form of a bolt held in a threaded aperture 32a at the striker end 32 of the latch arm 30. The striker 36 has a longitudinal axis X, and is held in place by a striker locking nut 38. The position of striker 36 within the latch arm 30 can be adjusted by screwing the striker 36 to the required position, and adjusting the locking nut 38. The connection end 34 defines a cylindrical aperture (not shown). The striker end 32 and the connection end 34 are substantially parallel to one another in this embodiment, and are separated by a central portion 35 that is at an angle of approximately 45° to the ends 32, 34, so that the latch arm 30 is cranked inboard.
The latch member 14 is pivotably connected to the housing 12 by a main shaft 40 that passes through the latch arm cylindrical aperture and the apertures of the latch member mounting point 26 to form a latch member pivot point 41. The latch member pivot point 41 has a longitudinal axis T (see
The latch arm 30 has a crossbar 31 positioned towards its connection end 34. The crossbar 31 defines a bore, within which is held a link shaft 33.
The latch member 14, handle 16 and striker 36 are in this embodiment made of zinc alloy, though other suitable materials may be used.
The latch 10 further comprises a linkage indicated generally at 62 (e.g. as shown in
Each first link 64 has a rounded first end 68 and a rounded second end 70. Each first end 68 defines a semi-circular aperture (not shown) that corresponds to the ends 58 of the handle shaft 54. The second end 70 defines a circular aperture (not shown). The first links 64 are positioned one on each end 58 of the handle shaft 54, with the first end 68 of each link 64 fitted over the handle shaft 54, so that the first links pivot together with the handle 16. The first link 64 on the same side of the handle shaft 54 as the spring 60 is positioned between the handle pivot point 56 and the spring 60.
Each second link 66 has a rounded first end 72 and a rounded second end 74. The first end 72 of each second link 66 is pivotably mounted to the second end 70 of the first link 64. The second end 74 defines a circular aperture configured to be pivotably mounted to the link shaft 33. The second links 66 are positioned one on each end of the link shaft 33 to form two second link pivot points 73. The second end 74 of each link 66 is pivotably fitted over the link shaft 33 and held in place by a shaft clip 75. The first end 72 of each second link 66 and the second end 70 of each respective first link 64 are pivotably connected by a shaft 76, forming two linkage pivot points 78 between the latch arm 30 and the housing body 18, i.e. outboard of the latch arm 30. The linkage 62 is therefore of the “four-bar” type, with the housing forming the fixed one of the bars.
In order for the latch 10 to be moved to the closed position, the handle 16 is pivoted about the handle pivot point 56. The first links 64 are pivoted about the handle pivot point 56 with the handle 16 in the direction Y (see
In this embodiment, distances and angles marked on
With the above geometry, the effect of the linkage 62 is that angular movement of the handle 16 results in lesser angular movement of the latch member 14. As the handle 16 travels further than the latch member 14, the amount of force applied to the handle 16 at a given location is less than the resultant force at an equivalent location on the latch member 14. This improves ease of operation of the latch 10. Another means of decreasing the force that need be applied would be to increase the length of the handle 16. The present invention advantageously provides a compact alternative to such a method.
Additional force may be required to fully close the latch 10, particularly if the latch 10 is used with a heavy closure or one which requires improved sealing. The most force will be required at the point where the latch member 14 contacts the closure surround 8. This may be referred to as the “active zone” and is taken to start when the latch member 14 is at approximately 11.3° to the housing body 18, i.e. where G=11.3°. At this point, the handle 16 is at approximately 15° to the body 18, i.e. H=15°. At G=0°, H=0°. To close, the latch member 14 must be pivoted through approximately 11.3°. The handle 16 is moved through approximately 15° in order to effect the movement of the latch member 14. The angular compression ratio at the active zone is therefore G/H, i.e. 1.33. That is, the amount of force applied at the striker 36 to the closure is 1.33 times the force applied by the user to the free end 46 of the handle 16.
For the pressure to be removed from the closure to allow the closure to be opened, the latch 10 must be released. The handle 16 can in this embodiment be pivoted to an angle H of 90° to the body 18, at which point the latch member 14 will be at an angle G of more than 80° to the body 18. This leaves suitable clearance between the latch member 14 and the closure surround 8. Clearance between the latch member 14 and the closure surround 8 is increased by the latch pivot point 41 being removed from the first edge 7 of the housing 12 in a direction parallel to the plane of the housing—i.e. further from this edge than the handle pivot point 56.
As previously stated, the measurements provided relate to an exemplary embodiment of the present invention. Other distances between pivot points can be used. However, the ratio of the distances used in this embodiment have been found to be optimal for the latch 10. Variation of the measurements can improve some features but hinder others. For example, increasing distances D or E would lead to an increase in the mechanical advantage but a decrease in the maximum angle G, i.e. a reduction in the clearance between the latch member 14 and the closure surround 8. Decreasing the distance B would do the same. Increasing distance F more than is needed for clearance is not believed to lead to a particular advantage and increases the minimum space required for the latch 10. Increasing the angle A to more than 165° can reduce the mechanical advantage and the fully open angle G. If the angle A is less than 165°, the first links 64 may impinge on the housing 12 as the handle 16 nears the closed position.
The latch 10 is shown in
The second latch member 85 is pivotably mounted to the closure 82 at a mounting point 87 by means of a second latch member shaft (not shown) that turns with the second latch member 85. The main shaft 40, about which the first latch member 14 pivots on operation of the handle 16, is fitted with a non-circular drive extension (not shown) at each end, each drive extension being configured to turn about the axis of the main shaft 40 (e.g. due to interference fit by virtue of a grub screw or a roll pin). An extension shaft 88 connects the second latch member shaft (not shown) to the main shaft 40 via one of the drive extensions. The second latch member 85 is thus pivoted in synchronisation with the first latch member 14 on operation of the latch 10 such that the striker 89 applies pressure to the closure simultaneously to the striker 36. As the main shaft 40 has more clearance from the closure 82 at the latch pivot point 41, the extension shaft 88 is also removed from the closure 82. This prevents damage being caused to the extension shaft 88 and the closure 82 during pivoting of the latch members 14, 85.
A second embodiment of the invention is shown in
The latch 110 of second embodiment of the invention is similar to that of the previous embodiment, except in that the handle 116 is L-shaped rather than T-shaped. The crossbar 117 of the “L” 116 extends towards the housing 112. The handle recess 121 is in this embodiment substantially rectangular, with indentations 127 on either side to allow the handle 116 to be grasped when in the closed position. The padlock loop 125 extends outboard, and is flanked in this embodiment by spring-loaded covers 139 set in the indentations 127. The covers 139 can be pushed inboard to allow a padlock (not shown) to be attached to the padlock loop 125. The handle recess 121 is deeper at one end to allow the handle 116 to be fully received the housing 12.
The latch member shaft 140 comprises in this embodiment square portions towards each of its ends. Extension shafts for satellite latch members, such as extension shafts 88, 94 of the previous embodiment, can thus be connected to the latch member shaft 140 without the need for further components.
A third embodiment of the invention is shown in
A fourth embodiment of the invention is shown in
A latch 310 is shown in an open position in
The linkage 362 of this embodiment differs to those of the previous embodiments. The first links 364 are at an angle of approximately 150° to the handle arm 344. As shown in
In use, rotation of the handle 316 from the open position shown in
As with the previous embodiments, the linkage 362 causes angular movement of the handle 316 to result in smaller angular movement of the latch member 314. As the handle 316 travels further than the latch member 314, the amount of force applied to the handle 316 is less than the resultant force at the latch member 314. The arrangement of the linkage 362 of this embodiment provides this mechanical advantage with a more compact linkage 362 than that of the previous embodiments. A compact linkage 362 is advantageous as there is often limited space inboard a latch. Over-centre motion of the linkage 362 is required for the latch 310 to move between the fully open and closed positions, which hinders forcing of the latch 310, and may remove the need for a separate biasing or retaining mechanism in some circumstances. Applying force to the handle 316 when the latch 310 is in the closed position causes the second links 366 to act against rotation of the first links 364, so helping to prevent opening of the latch 310.
The angular compression ratio at the active zone of this embodiment is on average 2.4. When the handle moves between 38° and 28°, the latch moves between about 4.6° to 0.5°, giving the average angular compression ratio of 2.4. That is, the amount of force applied at the free end 332 to the closure is 2.4 times the force applied by the user to the free end 346 of the handle 316.
A fifth embodiment of the invention is shown in
The latch member 414 is in this embodiment resiliently biased towards an open position by a biasing device (not shown). The latch 410 has two link members 463 having first and second ends 465, 467 and curved through 90°. The link members 463 are attached by an aperture (not shown) defined by the first end 465 to either side of the handle mounting point 423. The link members 463 are pivoted about the handle mounting point 423 together with the handle 416. The second ends 467 each define an aperture (not shown) and are connected to one another by a shaft 469. The latch arm 430 passes between the two link members 463, and is biased against the shaft 469.
The arrangement of this embodiment provides a simple method of latch operation, with the advantage of the latch pivot point 441 being spaced from the latch housing 412. This arrangement also results in a variation in mechanical advantage through the range of motion of the latch arm 430.
In an alternative to this embodiment (not shown), the latch arm 430 defines a slot through which a pin is held by the link members 463. The pin acts to move the latch arm 430 towards the open or closed positions, removing the need for the latch arm 430 to be biased towards the open position.
A sixth embodiment of the invention is shown in
The latch 510 of the sixth embodiment of the invention has a linkage 562 comprising a pair of links 564. The links 564 extend from the handle pivot point 556 to the latch member 514, where they are pivotably connected to a point 531 on the latch arm 530.
The connection end 534 of the latch member 514 is translatable as well as pivotable in the housing 512, as the latch member pivot point 541 is translatable with respect to the housing 512.
The latch member mounting point 526 of this embodiment comprises an opposing pair of slots 596. The slots 596 provide guide tracks for the latch member pivot point 541. Each end of the shaft 540 is supported within a respective slot 596, and is slidable along that slot 596. Each slot 596 has a first end 596a and a second end 596b. The first end 596a of each slot 596 has a dogleg 597 at an outboard side configured to receive the shaft 540 when the latch 510 is in the closed position, e.g. as shown in
In this embodiment, the latch member mounting point 526 is in the same piece of material as the padlock loop 525. Both of these features 526, 525 must be of relatively strong material, so it is advantageous to provide both as a single component. However, in alternative embodiments the mounting point 526 and padlock loop 525 may be separate pieces.
In use, as the handle 516 is moved from the closed position of
As with the previous embodiments of the invention the handle 516 moves a greater angular distance than the shaft member 514, so a force advantage is gained, and less force need be applied at the handle 516 than is required at the striker 536. The compressive force applied is greater at the active zone, i.e. when the latch is close to closure.
An additional advantage of this embodiment is that it is relatively compact. Restraint of the connection end 534 of the sixth embodiment by the guide tracks 596 means that pivoting of the latch member 514 is controlled, so the striker 536 does not travel as far inboard as in previous embodiments. Advantageously, less space is thus required in the often limited space inboard a latch. The shape of the slots 596 may be altered to change the path of motion of the latch member 514.
A seventh embodiment of the invention is shown in
As with the sixth embodiment, the latch 610 of this seventh embodiment of the invention has a linkage 662 comprising a pair of links 664. In contrast to the previous embodiments, the latch member 614 extends either side of the linkage 662. The linkage 662 comprises a linkage shaft 698, and the latch member 614 defines an opposing pair of curved slots 699 configured to received either end of the linkage shaft 698, providing guide tracks 699 for the linkage shaft 698. The latch member 614 is pivotable and slidable relative to the linkage shaft 699.
The slots 699 each have a first end 699a and a second end 699b. The first end 699a of each slot 699 has a dogleg 697 configured to receive the linkage shaft 698 when the latch 610 is in the closed position, e.g. as shown in
In use, as the handle 616 is moved from the closed position of
Once again, the handle 616 moves a greater angular distance than the shaft member 614, so a force advantage is gained, and less force need be applied at the handle 616 than is required at the striker 636. Again, the compressive force applied is greater at the active zone, i.e. when the latch is close to closure. As with the previous embodiment, the shape of the slots 699 may be altered to change the path of motion of the latch member 614.
In further embodiments of the invention (not shown) one or more of the above second, third, fourth, fifth, sixth or seventh embodiments are incorporated into a latch assembly as described in the first embodiment of the invention.
An eighth embodiment of the invention is shown in
The latch 710 of the seventh embodiment of the invention has a linkage 762 where the first link second ends 770 extend over the latch arm 730 when the latch 710 is in the closed position (e.g. as shown in
The second links 766 of this embodiment are connected to form a U-shape, with the arms of the U providing the second links 766 which are joined by the cross-bar 777 of the U. The first ends 772 of the second links 766 are proximal the cross-bar 777. When the latch 710 is moved from the closed position to the open position (as shown in
In this embodiment, the length of each first link 764 between the handle pivot point 756 and the linkage pivot point 778 is 51.5 mm. The length of each second link 766 between the second link pivot point 773 and the linkage pivot point 778 is in this embodiment 21 mm. These distances may be varied in alternative embodiments.
Over-centre motion of the linkage 762 is required for the latch 710 to move between the fully open and closed positions, which hinders forcing of the latch. Applying force to the handle 716 when the latch 710 is in the closed position causes the second links 766 to act against rotation of the first links 764, so helping to prevent opening of the latch 710.
The latch member 714 of this embodiment is pivotably connected to the housing 712 by a second linkage in the form of first 779 and second 781 connection members arranged to form a parallelogram linkage with the housing 712 and the latch member 714. The connection members 779, 781 are pivotably connected to the housing 712 at one end, and pivotably connected to the latch member 714 at another end, such that the latch member 714 is pivotable with respect to the housing 712. “Pivotable” in this case includes pivotable motion between the latch member 714 and the housing 712 even where relative angles between the two do not substantially change.
The first connection member 779 is pivotably connected to the latch member mounting point 726 at its first end 779a, and is pivotably connected at its second end 779b to the connection end 734 of the latch member 714 at a mounting point 755. The second connection member 781 is pivotably connected to the housing 712 at a mounting point 726a at its first end 781a, and is pivotably connected at its second end 781b to a mounting point (not shown) on the latch member 714 between the striker end 732 and the second link pivot point 773.
In this embodiment, distances between pivot points are as follows. The distance between the latch member mounting point 726 and mounting point 755, i.e. the length of the first connection member 779 between its pivot points, is 22 mm. The second connection member 781 is of the same length, i.e. the distance between the mounting point 726a and the second connection member mounting point on the latch member 714 is 22 mm. In alternative embodiments the connection members 779, 781 may be of different lengths.
The distance between the latch member mounting point 726 and the second connection member mounting point 726a in a direction substantially parallel to the plane of the housing 712 is also 22 mm. The distance between the first connection member mounting point 755 and the second connection member mounting point along the latch member 714 is again 22 mm. Again, these distances may be varied in alternative embodiments.
The latch member 714 of this embodiment defines a central longitudinal aperture (not shown) configured to receive the connection member second ends 779b, 781b at their respective mounting points. Each of the connection member second ends 779b, 781b defines an aperture (not shown) through which a shaft 757 extends in an interference fit. The ends of each shaft 757 are pivotably received in the connection member second end 779b, 781b mounting points.
The latch member 714 and connection members 779, 781 of this embodiment are of zinc alloy. The first and second links 764, 766 are of stainless steel. In other embodiments other suitable materials may be used.
The housing 712 of this embodiment has a stop 753 for the first connection member 779. The stop 753 is in the form of a projection adjacent the latch member mounting point 726, and is configured to prevent movement of the first connection member 779 beyond the closed position. The stop 753, through limiting movement of the first connection member 779, prevents movement of the latch member 714 beyond the closed position. In alternative embodiments, a stop may be provided for the second connection member 781 as well as or instead of for the first connection member 779. The connection members 779, 781 may have projections configured to contact the housing 712, or rotation of the shafts 757 may be limited by stops on the latch member 714, to limit movement of the connection members 779, 781.
When the handle 716 is operated to move the latch 710 from a closed to an open position, the latch member 714 is moved by the linkage 762 on the connection members 779, 781 towards the closed position. The connection members 779, 781 pivot about their respective mounting points 726, 726a and the latch member 714 describes a shallow arc as it moves from the open to the closed position. The connection members 779, 781 act to retain the latch member 714 relatively parallel to the housing 712 as it moves, so that protrusion of the striker end 732 inboard of the housing is advantageously restricted. The lengths and relative positions of the connection members 779, 781 can be altered to change the path of motion of the latch member 714.
When the latch member 714 reaches the closed position its movement is restricted by contact between the first connection member 779 and the stop 753, and/or between the striker 736 and the closure. The linkage 762 continues to be moved, after the latch member 714 has stopped, into an over-centre position, with the link pivot point 778 between the second link pivot point 773 and the striker 736 in a direction substantially parallel to the plane of the housing 712. Resistance to movement of the latch member 714 is required for the linkage 762 to be moved into the over-centre position. The stop 753 provides this resistance regardless of whether the latch member 714 reaches the closure. Correct fitting of the latch 710 need not, therefore, be relied upon for proper closing of the latch 710. Fluctuations in temperature that could affect the relationship between the latch 710 and the closure are also thus provided for.
The handle 716 moves a greater angular distance in relation to the housing 712 than the first and second connection members 779, 781, so a force advantage is gained, and less force need be applied at the handle 716 than is required at the striker 736. As in earlier embodiments, the compressive force applied is greater at the active zone, i.e. when the latch 710 is close to closure.
The relative angles K, L (see
In this embodiment the “active zone” starts when the connection members 779, 781 are at 41.3° to the plane of the housing 712. The connection members 779, 781 move through only 6.7° in the active zone to their datum of 34.6°, whilst the handle 716 moves through 15° to effect movement of the connection members 779, 781. The angular compression ratio at the active zone is therefore 15/6.7, i.e. 2.24. That is, the amount of force applied at the striker 736 to the closure is 2.24 times the force applied by the user to the free end 746 of the handle 716, assuming that the length between the free end 746 and the handle pivot point 756 is equal to length of each connection member 779, 781 between their respective pivot points. Where the handle 716 is longer than the connection members 779, 781, the amount of force applied at the striker 736 to the closure is proportionally greater than 2.24, and vice versa.
As shown in
The latch 710 is shown in
The latch member 714 comprises in this embodiment a pair of arms 743 extending parallel to the main body of the latch member 714. Each arm 743 provides a mounting point 745 for a link 749. In this embodiment, a link 749 extends between the mounting point 745 proximal the second latch member 785 and the extension shaft mounting point 747, and is connected to the extension shaft 788 at the extension shaft mounting point 747. The link 749 is configured to pivot about the extension shaft mounting point 747 and is controlled by movement of the latch member arm 743, so that as the latch member 714 moves between the open and closed positions the link 749 is pivoted at the same rate.
As the link 749 is pivoted about the extension shaft mounting point 747 by the latch member 714, the extension shaft 788 is turned by the link 749, causing the second latch member 785 to turn also. The second latch member 785 is thus pivoted in synchronisation with the latch member 714 between the open and closed positions such that the striker 789 applies pressure to the closure simultaneously to the striker 736. The extension shaft 788 is remote from the closure, preventing damage being caused to the extension shaft 788 and the closure during pivoting of the latch member 785.
In alternative embodiments further latch members may be provided, including a latch member or members perpendicular to the first and second latch members, as shown in
In yet further embodiments of the invention (not shown), the crank of the lever arm may be increased or decreased. The latch may be attached to a closure surround, rather than to a closure. Electronic locking of the latch may be used.
All of the above embodiments of the invention have the advantage of increased independence of motion between the handle and the latch member in comparison to a latch such as that shown in GB2264530. A further advantage of the invention is the distance between the latch member pivot point and the plane of the housing that can be provided by the independence of motion. This is particularly advantageous where a closure has a lip or other projection to be passed, such as that shown in FIG. 6—moving the latch member pivot point inboard removes the need to design the latch arm to pass over such a lip. Distance between the latch member pivot point and the plane of the housing also reduces rubbing of the striker along the closure surround during closure.
Further advantages include that the inboard and outboard (“dry” and “wet”) sides of the latch 10 are easily sealed from one another. Simple O-rings are all that are required for sealing of the inboard side.
A ninth embodiment of the invention is shown in
A latch assembly is indicated generally at 880 in
The latch assembly 880 also includes a secondary, satellite, latch 1010 and a drive shaft 1030 extending between the secondary latch 1010 and the primary latch 810. The drive shaft 1030 is configured to drive the secondary latch 1010, and is actuated by the primary latch 810. The drive shaft 1030 is thus actuated remotely, i.e. the point at which input to the drive shaft is provided is removed from the secondary latch 1010. For example, input is not provided by a handle positioned at the secondary latch 1010.
The secondary latch 1010 is pivotably mounted to an inside of a closure 809 by a latch mount 1012, described in further detail below. The mount 1012 has an outboard side 1020 proximal the closure 809 and an inboard side 1022 distal the closure 809. The drive shaft 1030 is rotatably connected to the mount 1012 at a first link pivot point 1032 which defines a first longitudinal axis M-M.
The secondary latch 1010 includes a latch member 1034 having a first end 1034a and a second end 1034b. The latch member first end 1034a is pivotably connected to the mount 1012 at a latch member pivot point 1036, which defines a second longitudinal axis N-N. The second longitudinal axis N-N is substantially parallel to the first longitudinal axis M-M.
The latch member 1034 comprises in this embodiment an elongate latch arm 1035 having two substantially parallel sides 1037. The latch arm 1035 is in this embodiment a single integral piece of sheet metal, the metal being stamped or cut to shape and folded to provide the sides 1037. In alternative embodiments other suitable types of latch arm may be used. The sides 1037 define corresponding substantially circular apertures 1049 proximal a latch arm first end 1035a, by which the latch member 1034 is pivotably connected to the mount 1012.
The latch member second end 1034b comprises a striker 1040. The striker 1040 of this embodiment is in the form of a bolt held in a threaded aperture (not shown) at a second end 1035b of the latch arm 1035. The striker 1040 is held in place by a striker locking nut 1041. The position of striker 1040 relative to the latch arm 1035 can be adjusted by screwing the striker 1040 to the required position, and adjusting the locking nut 1041.
The latch member 1034 is pivotable about the latch member pivot point 1036 between a closed position, in which the latch member 1034 is actuated to apply pressure to a closure surround 808, and a fully open position, where the latch member is clear of the closure surround 808. The latch 1010 is shown in
The latch member pivot point 1036 is remote from the first link pivot point 1032, and is inboard thereof, as shown in
The linkage 1038 is in this embodiment a four-bar linkage, and comprises a first link 1042 and a second link 1050. The first link 1042 is pivotably connected to the first link pivot point 1032. The first link 1042 comprises in this embodiment two opposing arms 1044, each defining an aperture 1046 configured to receive the drive shaft 1030. The first link 1042 is a single integral piece of sheet metal, the metal being stamped or cut to shape and folded to provide the arms 1044. In alternative embodiments, the link may be of two separate arms 1044, or other suitable materials and/or types of link may be used.
In this embodiment, the apertures 1046 are substantially square, and the drive shaft 1030 is correspondingly square where it is received by the first link 1042, so that the first link 1042 turns with the shaft 1030. In alternative embodiments (not shown), the apertures 1046 may correspond to some other non-circular drive shaft shape, or the first link 1042 may be keyed to the drive shaft 1030.
The first link arms 1044 each further define a linkage pivot point aperture 1048. The apertures 1048 are in this embodiment substantially circular, and are configured to pivotably receive the second link 1050, forming a linkage pivot point 1054.
The second link 1050 comprises in this embodiment a substantially U-shaped rod of substantially circular cross-section. A first arm 1050a of the second link extends pivotably through the apertures 1048 of the first link 1042 to form the linkage pivot point 1054 as described above. A second arm 1050b of the second link is pivotably connected to the latch member 1034 at a second link pivot point 1052. The latch arm 1035 defines a pair of corresponding substantially circular apertures 1051 through which the second arm 1050b extends to form the second link pivot point 1052. The second link pivot point 1052 is in this embodiment towards the latch arm first end 1035a, and the latch member pivot point 1036 is between the very end of the latch arm 1035a and the second link pivot point 1052. In alternative embodiments the second link pivot point 1052 may be elsewhere on the latch member 1034.
The second link 1050 extends through the first link 1042 and the latch member 1034 to form the linkage pivot point 1054 and the second link pivot point 1052 respectively. The need for separate pins at the pivot points is thus removed, advantageously reducing cost and increasing simplicity of the latch 1010.
The mount 1012 of this embodiment comprises a substantially planar body 1014 and two substantially parallel arms 1016 extending substantially perpendicular to the body 1014. The mount 1012 is in this embodiment a single integral piece of sheet metal, the metal being stamped or cut to shape and folded to provide the arms 1016. In alternative embodiments, other suitable types of mount may be used. The body 1014 defines an aperture 1018 at each end, configured to receive a fastener (not shown) by which the mount 1012 is secured to the closure 809. The mount 1012 is secured such that the arms 1016 extend inboard of the body 1014.
The mount arms 1016 define recesses 1060 configured to receive the linkage pivot point 1054. The recesses 1060 are open-ended, allowing the second link first arm 1050a to enter the recesses 1060 as the closed position is reached. The recesses 1060 support the linkage pivot point 1054 and may act as a stop, inhibiting over-rotation of the shaft 1030.
The arms 1016 each define a shaft aperture (not shown) configured to receive the shaft 1030 to form the first link pivot point 1032. The mount 1012 further comprises two inserts 1054, 1056 pivotably supported within the shaft apertures. Each insert 1054, 1056 defines a substantially square aperture 1058 configured to receive the shaft 1030, so that the inserts 1054, 1056 turn with the shaft 1030 in the mount 1012. The shaft 1030 is thus pivotably supported by the mount 1012.
In alternative embodiments (not shown), the apertures 1058 may correspond to some other non-circular drive shaft shape,
The shaft 1030 of this embodiment is configured to actuate only a single secondary latch 1010. The shaft 1030 therefore extends no further than the side of the mount 1012 distal the primary latch 810. The insert 1056 at this side of the mount 1012 is closed to cover an end 1030a of the shaft. In an embodiment where one or more further secondary latches 1010 are actuated by the drive shaft 1030, the insert 1056 of the distal side of the mount 1012 is identical to the other insert 1054, so that the shaft 1030 extends through both inserts 1054, 1056 to the next secondary latch 1010.
The linkage 1038 is configured such that rotation of the drive shaft 1030 results in smaller angular movement of the latch member 1034 at at least one position throughout its range of motion, as follows.
Rotation (or angular movement) of the drive shaft 1030 causes angular movement of the latch member 1034 via the linkage 1038. However, due to the remote positioning of the pivot points 1032, 1036, angular movement of the latch member 1034 is not constant in relation to rotation of the drive shaft 1030. When moving from the fully open position towards the closed position, the shaft 1030 rotates the first link 1042, which in turn rotates and moves the second link 1050, so that the latch member 1034 begins to move towards the closed position. At this starting point, a higher proportion of movement of the first arm 1050a is in the direction of the latch member closed position, due to the position of the first link 1034 on the shaft 1030. The first arm 1050a is therefore moved by rotation of the first link 1042 relatively quickly in the direction of the closed position, so that the latch member 1034 is moved relatively far in relation to movement of the drive shaft 1030.
As the first arm 1050a approaches the closed position (shown in
The ratio of the angular movement of the drive shaft 1030 to that of the latch member 1034 thus varies depending upon the angular position of the latch member 1034. The effect of this variation in relative movement of the latch member 1034 and the drive shaft 1030 is that the compression force of the latch member 1034 is also varied. Because the ratio of the angular movement of the drive shaft 1030 to that of the latch member 1034 is greater in the active zone compared to outside the active zone, the force of the latch member 1034 is greater in the active zone compared to outside the active zone. The latch member 1034 therefore advantageously applies increased compression to the closure surround 808, securing the closure.
For example, in the exemplary embodiment of the invention, the active zone is taken to be between the latch member 1034 being at approximately 10.1° to the closure 809, and the latch member 1034 being at substantially 0° to the closure, i.e. in the closed position. To close, therefore, the latch member must be pivoted through approximately 10.1°. in order to move the latch member 1034 through 10.1°, the drive shaft 1030 rotates through substantially 30°. The angular compression ratio at the active zone is therefore 30/10.1, i.e. 2.97.
As the latch member 1034 approaches the closed position, the angular compression ratio increases as shown in the table below. As shown, the amount of force applied at the striker 1040 to the closure surround 808 at a relative latch member angle of 0.84° is 4.18 times the force applied to the drive shaft 1030, and increases still further as the latch member 1034 moves towards the closed position.
As described in previous embodiments, the angular compression ratio of the handle 816 of the primary latch 810 to the primary latch member 814 is also increased in the active zone. As the drive shaft 1030 is in this embodiment driven by the primary latch member 814, the angular compression ratio between the handle 816 and the latch member 1034 of the secondary latch 1010 is thus increased further, in addition to the increase shown in the above table.
The linkage 1038 uses over-centre motion to move between the closed position and the fully open position. As the latch member 1034 reaches the closed position, the drive shaft 1030 continues to rotate, and the second link 1050 is pivoted by the first link 1042 with respect to the latch member 1034 so as to provide over-centre motion. The over-centre motion locks the latch member 1034 in position, maintaining the compressive force whilst substantially removing load from the shaft 1030. This advantageously increases the life of the shaft 1030, as it is subjected to torsional load only when the latch 1010 is being opened or closed, and not when the latch 1010 is in the closed position.
As described above, the drive shaft 1030 is actuated by the primary latch 810. In this embodiment, the drive shaft 1030 is actuated by movement of the latch member 814. In this embodiment, the secondary latch member 1010 is substantially parallel to the primary latch member 814. The latch assembly 880 includes a drive shaft link 1062 that provides a connection arrangement between the primary latch 810 and the secondary latch 1010. The drive shaft link 1062 is pivotably connected at a first end 1062a to the latch member 814, and connected at a second end 1062b to the drive shaft 1030. The second end 1062b is keyed to the shaft 1030, or defines a non-circular aperture (not shown) into which a corresponding non-circular part of the shaft 1030 extends, so that the shaft 1030 turns with the shaft link 1062b.
The drive shaft 1030 is supported at its second end 1030b by a shaft support 1064. The shaft support 1064 is fastened to the housing 812 by a fastener 1063 extending through a fixing pad 1065 and comprises a substantially parallel pair of arms 1066. The arms 1066 define corresponding substantially circular apertures 1068 configured to rotatably support the shaft second end 1030b.
The latch member 814 moves between an open and a closed position in an arc, moving the shaft link first end 1062a in an arc. The shaft link second end 1062b is thus pivoted, causing the shaft 1030 to rotate and to actuate the secondary latch 1010. The assembly 880 is arranged so that the primary latch 810 reaches the closed position after the secondary latch 1010. Force is thus applied to initially secure the closure 809 by the secondary latch 1010. However, in alternative embodiments, the latches 810, 1010 may close simultaneously, or the secondary latch 1010 may close after the primary latch 810 closes.
In alternative embodiments, the drive shaft 1030 may be actuated by movement of some other part of the primary latch 810, such as the handle 816.
The latch assembly 880 may include more than one secondary latch 1010. Further secondary latches 1010 may have latch members 1034 substantially parallel to the latch member 814 of the primary latch 810, and/or substantially perpendicular to the latch member 814 of the primary latch 810. Where a secondary latch 1010 has a latch member 1034 substantially perpendicular to, or at any other angle to, the latch member 814 of the primary latch, the latch assembly 880 includes a connection arrangement as described in relation to the latch assembly 80 and shown in
Multiple secondary latches 1010 may be actuated by a single drive shaft 1030, or more than one shaft 1030 may be used to actuate further secondary latches 1010.
In alternative embodiments, the secondary latch 1010 may be similar to a compression latch of one of the first eight embodiments.
The latch 1010 advantageously provides compression on a closure at a satellite latch point. The latch 1010 substantially removes torsional load on the drive shaft 1030 once the latch 1010 is in the closed position, whilst maintaining compression, due to the over-centre arrangement.
The latch member 1034, the latch mount 1012 and the first link 1042 are simply constructed from stamped and folded metal, and the second link 1050 is simply constructed from metal rod. The latch 1010 is thus relatively inexpensive to produce, and advantageously simple to assemble.
| Number | Date | Country | Kind |
|---|---|---|---|
| GB1210157.2 | Jun 2012 | GB | national |
| GB1305238.6 | Mar 2013 | GB | national |
