BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates generally to reels for spooling linear material, and specifically to hand cranks for reels.
2. Description of the Related Art
Reels for spooling linear materials, such as hose or wire, typically comprise a cylindrical drum and a means for rotating the drum. The linear material is spooled onto the drum as it is rotated.
Some reels are equipped with a motor for rotating the reel. However, in some cases motors add undesired cost, weight, and complexity to the reel. Another means for rotating the drum is a hand crank. A typical hand crank comprises an L-shaped handle coupled to a shaft. The shaft is ordinarily coupled to the reel such that the shaft is co-linear with the rotation axis of the drum. In this configuration, spinning of the shaft causes the drum to rotate about the drum rotation axis. The reel is rotated by moving the L-shaped handle in a circle to spin the shaft and thus rotate the drum.
Unfortunately, prior art hand cranks, such as the above-described L-shaped handle configuration, are somewhat difficult to use in practice. There is a need for a hand crank that is easier to use.
SUMMARY OF THE INVENTION
In one aspect of the invention, a system for spooling linear material is provided comprising a reel drum onto which linear material can be spooled and a lever pivotable about an axis. Additionally, the system comprises a torque transfer mechanism comprising an engagement clutch configured to engage and transfer a torque to the reel drum when operated in a first rotational direction, but configured to not operate nor transfer a torque to the reel drum when operated in a second rotational direction opposite the first rotational direction. The torque transfer mechanism is configured to convert back and forth pivoting of the lever into the rotation of the reel drum in the first rotational direction.
In another aspect of the invention, a method for rotating a reel drum onto which linear material can be spooled is provided. The method comprises the step of providing a lever pivotable in a first lever direction and a second lever direction opposite the first lever direction. The method also comprises the step of providing a torque transfer mechanism operatively coupled to the lever and to a reel drum. Additionally, the method comprises the steps of pivoting the lever in the first lever direction to transfer a torque generated form said pivoting of the lever onto the reel drum to rotate the reel drum in the first rotational direction, and pivoting the lever in the second lever direction to transfer a torque generated from said pivoting of the lever onto the reel drum to rotate the reel drum in the first rotational direction.
In still another aspect of the invention, a system for spooling linear material is provided, comprising a reel drum onto which a linear material can be spooled and a lever movable in a first direction and in a second direction opposite the first direction. The system also comprises means for converting the movement of the lever in said first and second directions into the rotation of the reel drum in a first rotational direction to spool said linear material onto the reel drum.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a perspective view of a reel for spooling linear material;
FIG. 2 is a side view of a reel having a preferred embodiment of a hand crank assembly.
FIG. 3 is a front view of the hand crank assembly of FIG. 2.
FIG. 4 is a perspective view of a reel having another preferred embodiment of a hand crank assembly.
FIG. 4A is an enlarged front view of an engagement clutch of the hand crank assembly shown in FIG. 4.
FIG. 4B is a side view of a portion of the engagement clutch shown in FIG. 4A.
FIG. 4C is a partial cross-sectional view of another embodiment of an engagement clutch for use with an embodiment of the hand crank assembly.
FIG. 5A is a front view of the hand crank assembly of FIG. 4.
FIG. 5B is a schematic configuration of a portion of one embodiment of a hand crank assembly.
FIG. 5C is a schematic configuration of a portion of another embodiment of a hand crank assembly.
FIGS. 6A and 6B are schematic drawings of the operation of the hand crank embodiment shown in FIG. 5B.
FIGS. 7A and 7B are schematic drawings of the operation of the hand crank embodiment shown in FIG. 5C.
FIG. 8 is a perspective view of a reel having another preferred embodiment of a hand crank assembly.
FIG. 8A is a front view of the hand crank assembly of FIG. 8.
FIGS. 9A and 9B are schematic drawings of the operation of the hand crank embodiment shown in FIGS. 8 and 8A.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
FIG. 1 shows a reel 5 of the type that can be equipped with a hand crank assembly, in accordance with any of the embodiments described herein. The reel 5 comprises a preferably cylindrical drum 10 and two disc-shaped side plates 12 and 14. The side plates 12 and 14 are affixed to opposite ends of the drum 10. Preferably, the side plates 12 and 14 are rigidly affixed to the drum 10, such that the elements 10, 12, and 14 rotate in unison about a rotation axis 16. In use, a linear material, such as hose or wire, is spooled onto the drum 10 by rotating the reel 5 about the rotation axis 16 and simultaneously causing the linear material to be wrapped around the drum 10. Such rotation can be effected by means of a hand crank coupled to the reel 5. The reel 5 is typically enclosed or housed inside a stable outer frame (not shown).
FIGS. 2 and 3 illustrate a preferred embodiment of a hand crank assembly 20. FIG. 2 shows a side view of the reel 5 of FIG. 1, wherein the hand crank assembly 20 is coupled to the reel 5 and positioned on the outer side of the side plate 14 (in the view of FIG. 1, to the right side of the side plate 14). FIG. 3 shows a front view of the hand crank assembly 20. In FIG. 3, the drum 10 and side plate 12 are omitted for clarity. If shown, the drum 10 and side plate 12 would be positioned to the left of the side plate 14. As described below, the reel 5 can advantageously be rotated continually in one direction about the rotation axis 16 by reciprocal back and forth pivoting movement of a lever 30 in the direction of the arrows 36 and 38.
As mentioned above, the reel 5 is preferably housed within a stable structure or frame. Examples of suitable housings and frame structures are disclosed in U.S. Pat. No. 6,279,848, which is hereby incorporated herein by reference. FIG. 3 depicts a frame portion 40, which can be a plate or crossbar. The housing or frame structure is preferably configured such that the frame portion 40 remains parallel to the side plate 14 as the side plate 14 rotates about the rotation axis 16. In FIG. 3, the top and bottom ends of the frame portion 40 are shown broken to indicate that the frame portion 40 extends as part of a larger structure. It will be understood that the housing and the illustrated frame portion 40 can have any of a large variety of shapes, sizes, and configurations. The frame portion 40 is omitted from FIG. 2 for clarity.
With reference to FIGS. 2 and 3, the hand crank assembly 20 comprises a first gear 22, a second gear 24, a first sprocket 26, a second sprocket 28, the lever 30, a chain 32, and a spring 34. The first gear 22 is coupled to the side plate 14 so that rotation of the first gear 22 in either direction about the axis 16 (FIG. 1) causes the side plate 14, and hence the entire reel 5, to rotate in the same direction about the axis 16. Preferably, the first gear 22 is rigidly affixed to the side plate 14 so that they rotate together in unison. The first sprocket 26 is coupled to the first gear 22 via a first one-way clutch mechanism. With reference to FIG. 2, the first one-way clutch is configured so that when the first sprocket 26 is rotated counter-clockwise, the first one-way clutch is engaged, thereby causing the first gear 22 to rotate counter-clockwise in unison with the first sprocket 26. However, when the first sprocket 26 is rotated clockwise, the first one-way clutch is disengaged, permitting the first sprocket 26 to rotate clockwise freely with respect to the first gear 22.
The second sprocket 28 is rotatably mounted onto the inner side of the frame portion 40 (as shown in FIG. 3, to the left side of the frame portion 40). The second gear 24 is coupled to the second sprocket 28 by a second one-way clutch mechanism. The directions of engagement and disengagement of the second one-way clutch are opposite to those of the first one-way clutch. With reference to FIG. 2, the second one-way clutch is configured so that the second one-way clutch is engaged when the second sprocket 28 is rotated clockwise, thereby causing the second gear 24 to rotate clockwise in unison with the second sprocket 28. However, when the second sprocket 28 is rotated counter-clockwise, the second one-way clutch is disengaged, permitting the second sprocket 28 to rotate counter-clockwise freely with respect to the second gear 24. An end of the lever 30 is coupled to the second sprocket 28 (in the illustrated embodiment, via a rod 31 extending through the frame portion 40), so that pivoting of the lever 30 in either of the directions 36 or 38 produces rotation of the second sprocket 28 in the same direction. Those of ordinary skill in the art will appreciate that the frame portion 40 could be on the other side of the lever 30 or on the other side of part or all of the hand crank assembly 20.
The first and second gears 22 and 24 have teeth that mesh together. Thus, rotation of one of the gears in one direction produces rotation of the other gear in the opposite direction. The sprockets 26 and 28 also have teeth, which engage the links of the chain 32. In the illustrated embodiment, the chain 32 has a first end fixed to the second sprocket 28. From that point, the chain 32 wraps around the first sprocket 26 and has a second end attached to a first end of the spring 34. The spring 34 has a second end fixed to the reel housing, perhaps to the frame portion 40. The chain 32 and the spring 34 are sized and configured so that, during normal operation of the crank assembly 20, the spring 34 is always somewhat stretched. The illustrated spring 34 is a coil spring. However, other suitable springs could be used alternatively.
As mentioned above, reciprocal back and forth movement, or pivoting, of the lever 30 causes the reel 5 to rotate continually in one direction and preferably drives the reel in that direction with each back movement and each forth movement. With respect to FIG. 2, in the illustrated embodiment, pivoting of the lever 30 in either direction 36 or 38 causes the reel 5 to rotate counter-clockwise. In order to appreciate this, consider separately the operation of the hand crank assembly 20 during motion of the lever 30 in the direction 36 and then in the direction 38.
With reference to FIG. 2, when a user moves the lever 30 in the direction 36, the second sprocket 28 rotates clockwise. This causes the second one-way clutch to engage. As a result, the second gear 24 rotates clockwise in unison with the second sprocket 28. The clockwise rotation of the second gear 24 produces counter-clockwise rotation of the first gear 22, due to the meshing of the teeth of the two gears. As mentioned above, the first gear 22 is coupled to the reel 5, producing counter-clockwise rotation of the reel. The counter-clockwise rotation of the first gear 22 does not cause the first one-way clutch to engage. Rather, the first one-way clutch remains disengaged. Thus, the counter-clockwise rotation of the first gear 22 does not affect the first sprocket 26, which is free to rotate clockwise. Further, since the second sprocket 28 rotates clockwise, the chain 32 tends to become slackened in the region between the two sprockets. However, the spring 34, which is always somewhat stretched, pulls the chain 32 (to the right in FIG. 2) until the chain becomes taut. As the chain 32 is pulled by the spring 34, the first sprocket 26 rotates clockwise to permit the tautening of the chain 32.
With continued reference to FIG. 2, when a user moves the lever 30 in the direction 38, the second sprocket 28 rotates counter-clockwise. This causes the second one-way clutch to disengage, so that the rotation of the second sprocket 28 does not affect the second gear 24. The counter-clockwise rotation of the second sprocket 28 pulls the chain 32 (which is taut as explained above), producing counter-clockwise rotation of the first sprocket 26. The counter-clockwise rotation of the first sprocket 26 causes the first one-way clutch to engage. This causes the first gear 22 to rotate counter-clockwise in unison with the first sprocket 26. Since the first gear 22 is coupled to the reel 5, the reel rotates counter-clockwise. It will be appreciated that the counter-clockwise rotation of the first gear 22 produces clockwise rotation of the second gear 24. However, this clockwise rotation of the second gear 24 does not affect the second sprocket 28, because the second one-way clutch remains disengaged.
Thus it will be appreciated by those of ordinary skill in the art that the hand crank assembly 20 permits continual rotation of the reel 5 in one direction, driven by each stroke of reciprocal back and forth movement of the lever 30. This hand crank configuration is considerably easier to operate than prior art hand cranks, such as an L-shaped handle coupled to the center of one of the side plates 12 and 14.
It will also be appreciated that the chain 32 can comprise a continuous loop and be looped around the two sprockets 26 and 28. In this alternative embodiment, the spring 34 is omitted from the design. Preferably, the chain 32 is looped around both sprockets so that the chain is always relatively taut.
Preferably, the reel 5 is provided with a disengaging mechanism for disengaging the lever 30 from the second sprocket 28 when the linear material is unwound from the reel. This permits the linear material to be freely unwound without causing movement of the lever 30. To appreciate the need for such a disengaging mechanism, consider FIG. 2. If the linear material is unwound from the reel 5, the reel begins to rotate clockwise. This causes the first gear 22 to rotate clockwise and engage the first sprocket 26. The resultant clockwise rotation of the first sprocket 26 pulls the chain 32 and causes the second sprocket 28 and lever 30 to also rotate clockwise (in the direction of arrow 36). If the lever 30 has a large length relative to the reel, as is desirable for greater ease of operation, the lever 30 may hit the ground during unwinding. At the very least, the lever 30 will continually rotate as the linear material is unwound from the reel 5. The above-mentioned disengaging mechanism overcomes this problem.
With reference to FIG. 3, one suitable type of disengaging mechanism involves employing a spline and groove interconnection between the rod 31 and the second sprocket 28. For example, the rod 31 can include a spline receivable within a groove on the inside of the second sprocket 28, such that the two elements transfer torque to one another only when the spline and groove are engaged. Thus, when the spline of the rod 31 is pulled out of the second sprocket 28, the unwinding of the linear material from the reel 5 does not affect the lever 30. In one such embodiment, a pair of cam-type washers are employed, one connected to the rod 31 and the other set against the frame portion 40 so that their inclined or cam surfaces confront one another. When the linear material begins to unwind, the resultant rotation of the lever 30 causes the cam-type washers to rotate against one another and the rod 31 to slide to the right (in the view of FIG. 3). This causes the spline and groove to disengage, permitting free rotation of the reel 5 as the linear material is unwound. When the user wants to subsequently spool the linear onto the reel 5, the lever 30 can then easily be “clicked” back into normal operation.
Skilled artisans will appreciate that the hand crank assembly 20 can easily be configured to produce continual clockwise (as opposed to counter-clockwise) rotation of the reel 5 (with reference to the view of FIG. 2). This can be accomplished simply by substituting oppositely configured one-way clutches (i.e., using one-way clutches that engage and disengage in the opposite directions) or simply by swapping the first gear 22/first sprocket 26 combination with the second gear 24/second sprocket 28 combination. In addition, the chain 32 and spring 34 would have to be inverted so that (with reference to FIG. 2) the spring 34 is on the left side of the gears and sprockets, and the chain 32 extends along the right sides of the two sprockets.
In an alternative embodiment, the reel may be configured to have a second hand crank assembly or a motor to drive the unwinding rotation of the reel. The second hand crank assembly or motor could be positioned on the opposite side of the reel (in FIG. 1, to the left of the side plate 12) and would be operatively coupled to the reel drum 10. A second hand crank assembly or motor would be especially useful for heavier linear materials, such as fire hose.
The reel 5 can also have a reciprocating mechanism for converting rotation of the reel drum 10 into reciprocal back and forth translation of a guide aperture for the linear material, the guide aperture being within the reel housing or frame. Translation of such a guide aperture across the reel drum 10 can facilitate more uniform spooling of the linear material onto the drum. The previously mentioned U.S. Pat. No. 6,279,848 discloses a reciprocating mechanism for such a guide aperture. Specifically, this patent discloses a spiral groove within one of the side plates (e.g., side plate 12 or 14 of FIG. 1 of the present application), wherein the groove interacts with other elements to produce the aforementioned reciprocal translation of the guide aperture. With reference to FIG. 1, the spiral groove mechanism of U.S. Pat. No. 6,279,848 could be employed on side plate 12. It should be noted that any of a variety of different types of reciprocating mechanisms, such as the spiral groove design of U.S. Pat. No. 6,279,848, can be employed.
The extent and rate of rotation of the reel 5 per each back and forth stroke of the lever 30 are determined by the relative sizes of the first and second gears and the first and second sprockets. The extent and rate of rotation of the reel 5 can be increased by selecting a second gear 24 and a second sprocket 28 that are relatively large compared to the first gear 22 and the first sprocket 26. The specific sizes and gear ratios of the gears and sprockets are a matter of design choice, which should be based upon the desired rotation displacement and speed characteristics of the reel 5.
FIGS. 4 through 5A illustrate another preferred embodiment of a hand crank assembly 50 for use with a reel 60 onto which linear material may be spooled. In the illustrated embodiment, the reel 60 has two side plates 62, 64 on either side of a reel drum 66. The reel 60 also preferably has a reel shaft 68 extending along the rotation axis of the reel R. Preferably, at least one end 68a of the reel shaft has a hollow portion 69.
The reel shaft 68 preferably selectively couples to a twisting engagement clutch 100 on one end of the reel shaft 68. The twisting engagement clutch 100 preferably comprises a driven part 102 fixed onto the reel shaft 68 and a driving part 104 fixed onto a first or driven shaft 110, wherein the driven shaft 110 is rotatably coupled to the reel shaft 68. In the illustrated embodiment, the driven shaft 110 has a bushing 112 on one end 110a, said bushing 112 configured to be inserted through a hole (not shown) in the driven part 102 of the twisting engagement clutch 100 and into the hollow portion 69 of the real shaft 68. The bushing 112 preferably rotates freely within the hollow portion 69.
In a preferred embodiment, the driving part 104 of the twisting engagement clutch 100 is preferably configured to move relative to the driven shaft 110 without rotating relative to the driven shaft 110. As illustrated in FIGS. 4A and 4B, the driving part 104 is preferably movably coupled to the driven shaft 110 so as to be laterally movable along the driven shaft 110. In one embodiment, a spline 110b on the driven shaft 110 slides within a key hole 104a in the driving part 104, thus substantially preventing the rotation of the driving part 104 relative to the driven shaft 110 as the driven shaft 110 rotates. However, other suitable mechanisms can be used to substantially prevent the rotation of the driving part 104 relative to the driven shaft 110.
With respect to FIGS. 4A and 5A, the operation of the engagement clutch 100 is now discussed. As shown in FIG. 5A, a spring 114, such as a coil spring, is preferably disposed between the driving part 104 of the engagement clutch 100 and a frame portion 116 of a housing that encloses the reel 60, a section of which is shown. The spring 114 is configured to apply a generally constant lateral force onto the driving part 104, so as to push the driven part 104 into a position substantially adjacent the driven part 102 of the engagement clutch 100. Accordingly, in a preferred embodiment, the driving and driven parts 104, 102 of the engagement clutch 100 are substantially adjacent each other during the use of the hand crank assembly 50. The spring 114 is preferably strong enough to constantly maintain the driving part 104 substantially adjacent the driven part 102.
As illustrated in FIGS. 4A-5A, the driving part 104 of the engagement clutch 100 preferably has teeth 104b configured to engage with teeth 102b of the driven part 102 when the driving and driven parts 104, 102 are generally adjacent each other. Preferably, the teeth 102b, 104b of the driven and driving parts 102, 104 are angled so that the driving part 104 meshes and transfers torque to the driven part 102 when rotated in a first rotational direction (e.g., clockwise), but does not mesh nor transfer torque when rotated in a second rotational direction (e.g., counter clockwise) opposite the first rotational direction. For example, consider the embodiment shown in FIG. 4A. When the driven shaft 100 is rotated in a clockwise direction (from the vantage of the right side of the drawing looking leftward), the driving part 104 also rotates in a clockwise direction due to the spline 110b and key hole 104a connection between the driving part 104 and the driven shaft 110. When rotated clockwise and while adjacent the driven part 102, the teeth 104b of the driving part 104 mesh with the teeth 102b of the driven part so as to transfer clockwise torque to the driven part 102, causing the driven part 102, and the reel shaft 68 attached to it, to rotate clockwise. Accordingly, the torque from the driving part 104 is transferred to the reel shaft 68 to rotate the reel drum 66. However, even when adjacent the driven part 102, if the driving part 104 rotates counter clockwise relative to the driven part 102, the teeth of the driving part 104 will slip relative to the teeth 102a of the driven part 102, so that no torque is transferred between the driving and driven parts 104, 102. One of ordinary skill in the art will recognize that the engagement clutch 100 described above may be used with the embodiment of the hand crank assembly described above with respect to FIGS. 2 and 3. For example, instead of having the first gear 22 coupled to the side plate 14, the first gear 22 may be coupled to the driving part 104 of the engagement clutch 100, while the driven part 102 of the engagement clutch 100 is coupled to a reel shaft of the reel 5.
FIG. 4C illustrates another embodiment of a twisting engagement clutch 100. The engagement clutch 100 includes a collar 106, which is disposed about a portion of the driving part 104. The collar 106 preferably houses a one-way clutch 108 configured to engage in the first rotational direction, but spin freely, or slip, in the second rotational direction opposite the first rotational direction. In the illustrated embodiment, the one way clutch 108 is configured to engage when rotated in the clockwise direction (from the vantage of the right side of the drawing looking leftward), but to spin freely or slip in the counter clockwise direction.
The one-way clutch 108 couples to a resistance bushing 108a disposed about a portion of the driving part 104. The resistance bushing 108a preferably has a surface that substantially contacts the portion of the driving part 104, and which provides resistance to the rotation of the driving part 104 relative to the bushing 108a. Accordingly, in a preferred embodiment, the driving part 104 and the one-way clutch 108 rotate at generally the same rate. More preferably, the surface of the resistance bushing 108a readily allows translation of the driving part 104 therethrough.
In the illustrated embodiment, the driven shaft 110 has a threaded portion 10b, which engages with threads 104c on the driving part of the engagement clutch 100. Preferably, the threads on the threaded portion 110 and the threads 104c on the driving part 104 are oriented such that rotation of the threaded portion 110 in the first rotational direction applies a forward driving force to the driving part 104. Additionally, a spring 109, such as a torsion spring, couples the driven shaft 110 to the driving part 104, with one end 109a of the spring 109 fastened to the driven shaft 110 and the other end 109b of the spring 109 fastened to the driving part 104.
With further reference to FIG. 4C, the operation of the illustrated embodiment of the engagement clutch 100 is discussed below. The hand crank assembly 50 is operated to rotate the driven shaft 110 in the first rotational direction, as discussed below. In one embodiment, the first rotational direction is the clockwise direction. As illustrated in FIG. 4C, rotation of the driven shaft 110 in a clockwise direction rotates the threaded portion 110b clockwise. The threaded portion 110b engages the threads 104c of the driven part 104 and exerts a forward driving force on the driving part 104. The surface of the bushing 108a provides sufficient resistance to the clockwise rotation of the driving part 104 to allow the driving part 104 to translate forward relative to the threaded portion 110 as the driving part 104 rotates along with the one-way clutch 108. Moreover, the resistance provided by the bushing 108a, along with the forward driving force provided by the threaded portion 110, overcomes a retraction force applied by the spring 109 in a direction opposite the forward driving force, so that the driving part 104 moves forward into substantial engagement with the driven part 102. Once the driving and driven parts 104, 102 are substantially engaged, the torque applied to the driven shaft 110 to rotate it clockwise is transferred to the driven part 102 and onto the reel shaft 68 for rotation of the reel drum 66 in the clockwise direction.
As noted above, in a preferred embodiment, the forward driving force provided by the threaded portion 110 along with the resistance provided by the bushing 108a overcome the retraction force applied by the spring 109 to move the driving part 104 forward. Once the driven shaft 110 is no longer rotated, the retraction force applied by the spring 109 overcomes the resistance force applied by the bushing 108a and retracts the driving part 104 through the bushing 108a, rotating the driving part 104 counter clockwise out of engagement with the driven part 102. The one-way clutch 108 slips or spins in the counter clockwise direction, thus allowing the driving part to be readily retracted onto the threaded portion 110b.
One of ordinary skill in the art will recognize that the embodiment of the engagement clutch 100 illustrated in FIG. 4C, and discussed above, can be used with any of the embodiments disclosed herein for a hand crank assembly 50. For example, the illustrated embodiment of the engagement clutch 100 can be used with the embodiments of the hand crank assembly 50 illustrated in FIGS. 5A and 8A, without the need to use the spring 114 to urge the driving and driven 104, 102 parts into engagement. One of ordinary skill in the art will also recognize that other suitable means can be used for transferring torque from the driven shaft 110 to the reel shaft 68 when rotated in the first rotational direction, but to disengage the driven shaft 110 from the reel shaft 68 when the driven shaft 110 is not rotated.
As shown in FIGS. 4 and 5a, a first pulley member 150 and a second pulley member 152 are preferably rigidly coupled to the driven shaft 110, each of said first and second pulley members 150, 152 configured to transfer a torque onto the driven shaft 110, as discussed further below. In the illustrated embodiment, the first pulley member 150 is operatively coupled to a third pulley member 154 via a first belt 160. Similarly, the second pulley member 152 is operatively coupled to a fourth pulley member 156 via a second belt 162. The third and fourth pulley members 154, 156 are coupled to a second or driving shaft 170. A lever 180 is coupled to one end 170a of the driving shaft 170.
As illustrated in FIGS. 5B, 6A and 6B, in one embodiment of the hand crank assembly 50, the first and second pulley members 150, 152 are disposed on either side of a first one-way clutch 200 coupled to the driven shaft 110. The first one-way clutch 200 is configured to operate in a first rotational direction, but not in a second rotational direction opposite said first rotational direction. For example, in the illustrated embodiment, the first one-way clutch 200 is configured to engage and operate in a clockwise (CW) direction, but not in a counter-clockwise (CCW) direction. Similarly, the third and fourth pulley members 154, 156 are disposed on either side of a second one-way clutch 210 coupled to the driving shaft 170. For example, in the illustrated embodiment, the second one-way clutch 210 is configured to engage and operate in a counter-clockwise (CCW) direction, but not in a clockwise (CW) direction.
As shown in FIG. 6A, when the lever 180 is moved or pivoted in a first lever direction (e.g., a clockwise direction), the fourth pulley member 156 rotates in the clockwise direction as well because it is coupled to the driving shaft 170. However, because the second one-way clutch 210 only operates in the counter clock-wise direction, rotation of the section of the driving shaft 170 to which the fourth pulley member 156 is attached is not transferred onto a second section of the driving shaft 170 to which the third pulley member 154 is coupled. Accordingly, the third pulley member 154 is not affected by the clockwise rotation of the lever 180. The clockwise rotation of the fourth pulley member 156 results in the clockwise rotation of the second pulley member 152 via the motion of the second belt 162, which converts the clockwise rotation of the fourth pulley member 156 into the clockwise rotation of the second pulley member 152. The clockwise rotation of the second pulley member 152 is subsequently transferred to the first pulley member 150 via the first one-way clutch 200, which transfers the torque from the second pulley member 152 onto the first pulley member 150. The driven shaft 110 also rotates clockwise since it is coupled to the first one-way clutch 200. The clockwise rotation is then transferred to the reel shaft 68 via the engagement clutch 100 (see FIG. 5A) to rotate the reel 60 in the first rotational direction (i.e., clockwise). The clockwise rotation of the first pulley member 150 causes the third pulley member 154 to rotate counter clockwise due to the belt 160. The second one-way clutch 210 remains disengaged as the third pulley member 154 rotates counter clockwise and the fourth pulley member 156 rotates clockwise.
As shown in FIG. 6B, when the lever 180 is moved or pivoted in a second lever direction (e.g., a counter clockwise direction), the fourth pulley member 156 rotates in the counter clockwise direction as well because it is coupled to the driving shaft 170. However, because the second one-way clutch 210 operates in the counter clock-wise direction, the rotation of the section of the driving shaft 170 to which the fourth pulley member 156 is attached is transferred onto a second section of the driving shaft 170 to which the third pulley member 154 is coupled. Accordingly, the third pulley member 154 also rotates counter clockwise. The counter clockwise rotation of the fourth pulley member 156 results in the counter clockwise rotation of the second pulley member 152 via the motion of the second belt 162. However, the counter clockwise rotation of the second pulley member 152 is not transferred to the first pulley member 150 via the first one-way clutch 200, which engages and operates only in a clockwise direction. The counter clockwise rotation of the third pulley member 154 results in the clockwise rotation of the first pulley member 150 via the motion of the first belt 160, which converts the counter clockwise rotation of the third pulley member 156 into the clockwise rotation of the first pulley member 150. The clockwise rotation is then transferred to the reel shaft 68 via the engagement clutch 100 (see FIG. 5A) to rotate the reel 60 in a first rotational direction (i.e., clockwise). The clockwise rotation of the first pulley member 150 does not affect the second pulley member 152 because the first one-way clutch 200 remains disengaged as the first pulley member 150 rotates clockwise and the second pulley member 152 rotates counter clockwise.
As illustrated in FIGS. 5C, 7A and 7B, in another embodiment of the hand crank assembly 50, the fourth pulley member 156 is coupled to the driving shaft 170 via the first one way clutch 200, while the third pulley member 154 is coupled to the driving shaft 170 via the second one-way clutch 210. In the illustrated embodiment, the first one-way clutch 200 is configured to engage and operate in a clockwise (CW) direction, but not in a counter-clockwise (CCW) direction.
As shown in FIG. 7A, when the lever 180 is moved or pivoted in a first lever direction (e.g., a clockwise direction), the fourth pulley member 156 rotates in the clockwise direction as well because it is coupled to the driving shaft 170 via the first one-way clutch 200, which engages and operates in the clockwise direction. However, because the second one-way clutch 210 only operates in the counter clock-wise direction, the clockwise rotation of the driving shaft 170 via the lever 180 is not transferred onto the third pulley member 154. Accordingly, the third pulley member 154 is not affected by the clockwise rotation of the lever 180. The clockwise rotation of the fourth pulley member 156 results in the clockwise rotation of the second pulley member 152 via the motion of the second belt 162, which converts the clockwise rotation of the fourth pulley member 156 into the clockwise rotation of the second pulley member 152. The clockwise rotation of the second pulley member 152 also results in the clockwise rotation of the first pulley member 150 since both the first and second pulley members 150, 152 are substantially rigidly fixed on the driven shaft 110. The clockwise rotation is then transferred to the reel shaft 68 via the engagement clutch 100 (see FIG. 5A) to rotate the reel 60 in the first rotational direction (i.e., clockwise). The clockwise rotation of the first pulley member 150 causes the third pulley member 154 to rotate counter clockwise due to the belt 160. The second one-way clutch 210 remains disengaged as the third pulley member 154 rotates counter clockwise and the fourth pulley member 156 rotates clockwise.
As shown in FIG. 7B, when the lever 180 is moved or pivoted in a second lever direction (e.g., a counter clockwise direction), the fourth pulley member 156 does not rotate in the counter clockwise direction because it is coupled to the driving shaft 170 via the first one-way clutch, which does not operate in the counter clockwise direction. However, because the second one-way clutch 210 operates in the counter clock-wise direction, the counter clockwise rotation of the driving shaft 170 via the lever 180 is transferred onto the third pulley member 154. Accordingly, the third pulley member 154 also rotates counter clockwise. The counter clockwise rotation of the third pulley member 154 results in the clockwise rotation of the first pulley member 150 via the motion of the first belt 160, which converts the counter clockwise rotation of the third pulley member 156 into the clockwise rotation of the first pulley member 150. The clockwise rotation is then transferred to the reel shaft 68 via the engagement clutch 100 (see FIG. 5A) to rotate the reel 60 in a first rotational direction (i.e., clockwise). The clockwise rotation of the first pulley member 150 also causes the second pulley member 152 and fourth pulley member 152 to rotate clockwise. The clockwise rotation of the fourth pulley member 156 does not conflict with the counter clockwise rotation of the lever 180 because the first one-way clutch 200 remains disengaged.
FIGS. 8 and 8A illustrate still another preferred embodiment of a hand crank assembly 50 for use with a reel 60 onto which linear material may be spooled. The illustrated embodiment is similar to the embodiment illustrated in FIGS. 4 and 5A, except as discussed below.
As illustrated in the embodiment shown in FIGS. 8A, 9A and 9B, the first and second pulley members 150, 152 are coupled to the driven shaft 110 via a first and second one-way clutch 220a, 220b, respectively. The one-way clutches 220a, b are preferably configured to operate in a first rotational direction, but not in a second rotational direction opposite said first rotational direction. That is, the one-way clutches 220a, b can engage and transfer torque in the first rotational direction, but slip and do not transfer torque in the second rotational direction. For example, in the illustrated embodiment, the one-way clutches 200a, b are configured to engage and operate in a clockwise (CW) direction, but not in a counter-clockwise (CCW). The third and fourth pulley members 154, 156 are rigidly coupled to the driving shaft 170.
With further reference to the embodiment illustrated in FIGS. 8 and 8A, the first belt 160 couples the first and third pulley members 150, 154. However, unlike the embodiment illustrated in FIG. 4, the first belt 160 does not extend completely around the first and third pulley members 150, 154. Instead, the first belt 160 is fastened at a location on the first and third pulley members 150, 154. Likewise, the second belt 162 couples the second and fourth pulley members 152, 156. However, the second belt 162 does not extend completely around the second and fourth pulley members 152, 156. Instead, the second belt 162 is fastened at a location on the second and fourth pulley members 152, 156.
As shown in FIG. 8a, the first pulley member 150 is preferably coupled to the frame portion 116 of the housing via a first torsion spring 114b. Preferably, the first torsion spring 114b is pre-tensioned so as to maintain the first belt 160 in a taut position. For example, if the first belt 160 slackens due to the rotation of the third pulley member 154, the first torsion spring 114b applies a torque to the first pulley member 150, rotating the first pulley member 150 in the same direction as the third pulley member 154 to take up said slack. Similarly, the second pulley member 152 is preferably coupled to a second frame portion 118 of the housing via a second torsion spring 114c. Preferably, the second torsion spring 114c is pre-tensioned so as to maintain the second belt 162 in a taut position. For example, if the second belt 162 slackens due to the rotation of the fourth pulley member 156, the second torsion spring 114c applies a torque to the second pulley member 152, rotating the second pulley member 152 in the same direction as the fourth pulley member 156 to take up said slack.
As shown in FIG. 9A, when the lever 180 is moved or pivoted in a first lever direction (e.g., a clockwise direction), the fourth pulley member 156 rotates clockwise as well because it is coupled to the driving shaft 170, which also rotates clockwise. The third pulley member 154 also rotates clockwise because it is coupled to the driving shaft 170, which causes the first belt 160 to slacken. However, the pre-tensioned first torsion spring 114b takes up the slack by rotating the first pulley member 150 counter clockwise. The counter clockwise rotation of the first pulley member 150 is not transferred to the driven shaft 110 because the first one-way clutch 220a engages in the clockwise direction, but slips in the counter clockwise direction. The clockwise rotation of the fourth pulley member 156 pulls the second belt 162 so as to rotate the second pulley member 152 clockwise. This in turn causes the driven shaft 110 to also rotate clockwise since the second one-way clutch 220b is configured to engage in the clockwise direction. The torque from the rotating driven shaft 110 is then transferred to the reel shaft 68 via the twisting engagement clutch 100 as discussed above.
As shown in FIG. 9B, when the lever 180 is moved or pivoted in a second rotational direction (e.g., a counter clockwise direction), the fourth pulley member 156 rotates counter clockwise as well because it is coupled to the driving shaft 170, which also rotates counter clockwise. The third pulley member 154 also rotates counter clockwise because it is coupled to the driving shaft 170, which pulls the first belt 160, causing the first pulley member 150 to rotate clockwise. The clockwise rotation of the first pulley member in turn causes the driven shaft 110 to also rotate clockwise since the first one-way clutch 220a is configured to engage in the clockwise direction. The torque from the rotating driven shaft 110 is then transferred to the reel shaft 68 via the twisting engagement clutch 100 as discussed above. The counter clockwise rotation of the fourth pulley member 156 causes the second belt 162 to slacken. However, the pre-tensioned second torsion spring 114c takes up the slack by rotating the second pulley member 152 counter clockwise. The counter clockwise rotation of the second pulley member 152 is not transferred to the driven shaft 110 because the second one-way clutch 220b engages in the clockwise direction, but slips in the counter clockwise direction.
One of ordinary skill in the art will recognize that the twisting engagement clutch 100 provides for easily unspooling of linear material from the reel drum 66 without affecting the operation of the hand crank assembly 50. Accordingly, the hand crank assembly advantageously provides for the efficient spooling of linear material onto the reel drum via the movement of a lever, while also allowing the reel to be rotated so as to unspool the linear material from the reel without any effect on the hand crank assembly.
One of ordinary skill in the art will readily recognize that the hand crank assembly 50 embodiments disclosed herein can be modified or arranged in any suitable way to result in the rotation of the reel drum in a desired direction. For example, as illustrated in FIGS. 6A through 7B, the embodiments of the hand crank assembly 50 illustrated herein are configured to rotate the reel drum in a clockwise direction upon the pivoting or movement of the lever 180. However, the hand crank assembly 50 can easily be arranged or modified to result in the counterclockwise rotation of the reel drum 66. For example, the first and second one-way clutches 200, 210 can be chosen such that the movement of the lever 180 in the first and second lever directions results in the counterclockwise rotation of the reel shaft 68 and the resulting counterclockwise rotation of the reel drum 66. Additionally, the belts connecting the first and second pulley members 150, 152 with the third and fourth pulley members 154, 156 can be replaced with other suitable means, such as chains, to transfer the rotation of the third and/or fourth pulley members 154, 156 onto the first and/or second pulley members 150, 152.
Although this invention has been disclosed in the context of certain preferred embodiments and examples, it will be understood by those skilled in the art that the present invention extends beyond the specifically disclosed embodiments to other alternative embodiments and/or uses of the invention and obvious modifications and equivalents thereof. Further, the various features of this invention can be used alone, or in combination with other features of this invention other than as expressly described above. Thus, it is intended that the scope of the present invention herein disclosed should not be limited by the particular disclosed embodiments described above, but should be determined only by a fair reading of the claims that follow.
Patent Application
20050087645
