CN106826646B

CN106826646B - Torque amplifying device

Info

Publication number: CN106826646B
Application number: CN201710061171.9A
Authority: CN
Inventors: 士丹利·D·温纳德
Original assignee: Shi DanliDWennade
Current assignee: Shi DanliDWennade
Priority date: 2009-07-31
Filing date: 2009-12-01
Publication date: 2020-03-17
Anticipated expiration: 2029-12-01
Also published as: TW201521965A; CN106826646A; TWI490090B; TW201307009A; CN104760014A; TWI487598B; TWI594849B; TWI601603B; TW201307011A; TWI496665B; TW201605583A; TW201615355A; CN101987441B; TWI573668B; TW201307006A; TW201307007A; TWI593517B; CN104760014B; TWI490089B; TW201103707A

Abstract

The present invention includes a torque multiplying ratchet device having a handle extending from a ratchet head. The ratchet head includes a hollow interior and a set of end face drive wheels disposed in the hollow interior, including a direction selection mechanism operatively connected to the set of end face drive wheels for selecting a direction of rotation and a socket engaging portion connected to the second face of the lower drive wheel and positioned to extend out of the hollow interior for removably receiving a socket.

Description

Torque amplifying device

The application is as follows: the divisional application with the application number of 201510187767.4, the application date of 2009, 12 months and 1 days, and the invention name of "torque amplification device". The parent application is a divisional application with application number 200910246904.1, application date 2009, 12/1, and the name "torque amplification device".

Technical Field

The present invention relates generally to the field of ratchet drives for driving screws, bolts, nuts and the like, and more particularly to reversible ratchet gear drives.

Background

Without limiting the scope of the invention, its background is described in connection with gears for tools and other instruments.

U.S. patent No. 7,413,065, the contents of which are incorporated herein by reference, discloses a ratchet mechanism for a hand tool. The mechanism includes a housing having a central opening and a pair of slots on opposite sides of the central opening. Each slot has an arcuate or rounded end opposite the central opening, the ends defining an arc of more than 180 degrees to pivotally retain a generally circular shank of a pawl therein. Because a pair of biasing members are provided in the housing, each pawl is biased inwardly toward the central opening and into engagement with teeth on an outer surface of a gear rotatably disposed within the central opening. A cover rotatably coupled to the housing over the pawls and the central opening can selectively disengage one of the pawls to allow the gear to rotate in a particular direction within the central opening.

US patent 7,409,884, the contents of which are incorporated herein by reference, discloses a torque transfer mechanism that connects an input shaft to an output shaft in order to transfer rotation and torque from the input shaft to the output shaft in either direction. The torque transfer mechanism also inhibits the transfer of rotation and torque from the output shaft to the input shaft in at least one direction.

For example, U.S. patent No. 7,347,124, the contents of which are incorporated herein by reference, discloses a transmission tool kit including a shaft having a longitudinal axis, the shaft having a driving end and a driven end. The driven end of the shaft is flexible relative to the driving end of the shaft to allow the driven end of the shaft to displace in an arcuate path relative to the driving end of the shaft. A torque-transmitting mechanism is drivingly connected to the driven end of the shaft.

U.S. patent No. 4,730,960, the contents of which are incorporated herein by reference, discloses a flexible sleeve extension. The extension structure includes a pair of end caps connected by a flexible cord, with one of the end caps engaging a female fitting, such as a sleeve.

US patent 4,680,994, the contents of which are incorporated herein by reference, discloses a quick socket wrench that significantly reduces the amount of work required to remove a nut or bolt. The spanner comprises a bevel gear and a matched small bevel gear, which are respectively arranged on a gear shaft and a small gear shaft, wherein the outer end of the small gear shaft is provided with a transmission shaft. A locking cap is located on the outer end of the drive shaft for releasably locking the drive shaft against rotation. The gears of the wrench are free to rotate in either direction and the gear ratio and gear size can vary with wrench size.

Another example includes a continuously variable transmission for use in machines and vehicles that apply rotary or linear power as disclosed in US7,419,451. The transmission may be used in vehicles such as automobiles, motorcycles, and bicycles. The transmission may be driven by a power transmission mechanism such as a sprocket, gear, pulley or lever, optionally driving a one-way clutch mounted on one end of the main shaft.

Disclosure of Invention

The invention provides a transmission wheel set for transmitting torque. The drive wheel set includes one or more intermediate drive wheels positioned between the upper drive wheel and the lower drive wheel to transmit torque from the upper drive wheel to the lower drive wheel. Each of the one or more double-sided intermediate end face drive wheels includes an at least partially textured intermediate drive wheel first face configured to engage the at least partially textured upper drive wheel face and located on an opposite side of the at least partially textured intermediate drive wheel second face. The lower drive wheel includes an at least partially textured lower drive wheel face configured to engage the at least partially textured intermediate drive wheel second face.

The invention provides a torque multiplication ratchet wheel device. The ratchet device includes a handle extending from a ratchet head. The ratchet head includes a hollow interior, a set of end face drive wheels disposed in the hollow interior, a direction selection mechanism operatively connected to the set of end face drive wheels for selecting a direction of rotation, and a sleeve engagement portion connected to the second face of the lower drive wheel and configured to extend from the hollow interior for removably receiving the sleeve. The set of end face drive wheels includes an upper drive wheel, an intermediate drive wheel, and a lower drive wheel, wherein the upper drive wheel has a first face connected to the ratchet head and opposite a second face of the upper drive wheel, the intermediate drive wheel includes a first face of the intermediate drive wheel, the first face of the intermediate drive wheel is opposite the second face of the intermediate drive wheel and selectively engages the second face of the upper drive wheel, the lower drive wheel includes a first face of the lower drive wheel, the first face of the lower drive wheel is opposite the second face of the lower drive wheel connected to the ratchet head, and wherein the second face of the intermediate drive wheel selectively engages the first face of the lower drive wheel. In operation, torque is transmitted from the ratchet head to the socket joint via the set of end face drive wheels at different rotation ratios.

In one embodiment, the face pulley has a plurality of teeth extending from the outer edge of the pulley to the center of the pulley, the height, slope and spacing of the teeth being application specific. In other embodiments, the set of face gears may have a splined surface, face gear, clutching structure, ribbed surface, textured surface, undulating surface, twill surface, linear surface, grooved surface, meshing surface, toothed surface, peened surface, smooth surface, rough surface, sticky surface, or other surface suitable for allowing friction between the surfaces. A direction selection mechanism moves the pawl engaging the intermediate drive wheel to select the direction of rotation of the set of end face drive wheels. The direction selection mechanism moves the intermediate transmission wheel to engage the upper transmission wheel or the lower transmission wheel, thereby selecting the rotation direction of the group of end surface transmission wheels. The ratchet device may also include a shaft extending from the ratchet head to a socket engagement portion, a separator ball disposed within an opening in the socket engagement portion, the socket engagement portion extending into the shaft; a stem including at least one socket, the stem extending into the shaft and reaching the sleeve engagement; a button on the ratchet head and connected to the stem, wherein depressing the button moves the stem downward, allowing the separator ball to move toward the stem into the at least one recess. The sleeve engagement portion may also be replaceable so that it can have different drive sizes like a spline drive.

The invention also provides a manufacturing method of the ratchet device, which comprises the following steps: inserting a set of end face drive wheels into the hollow interior of the ratchet head, wherein the set of end face drive wheels includes an upper drive wheel having an upper drive wheel first face connected to the ratchet head, an intermediate drive wheel including an intermediate drive wheel first face located opposite the upper drive wheel second face, the intermediate drive wheel first face located opposite the intermediate drive wheel second face and selectively engaging the upper drive wheel second face, and a lower drive wheel including a lower drive wheel first face located opposite the lower drive wheel second face connected to the ratchet head, and the intermediate drive wheel second face selectively engaging the lower drive wheel first face and the socket joint being connected to the lower drive wheel second face; positioning the direction selection mechanism to contact the set of end face transmission wheels so as to select a rotation direction; positioning the socket engagement portion to extend from the hollow interior cavity to removably receive a socket, wherein torque is transmitted from the ratchet head to the socket engagement portion via the set of end face drive wheels at different rotational ratios; the hollow inner cavity of the ratchet head is covered by a cover plate. In one embodiment, the face pulley has a plurality of teeth extending from the outer edge of the pulley to the center of the pulley, the height, slope and spacing of the teeth being application specific. In other embodiments, the set of face gears may have a splined surface, face gear, clutching structure, ribbed surface, textured surface, undulating surface, twill surface, linear surface, grooved surface, meshing surface, toothed surface, peened surface, smooth surface, rough surface, sticky surface, or other surface suitable for allowing friction between the surfaces. The sleeve engagement portion is replaceable with a different sized sleeve engagement portion.

The invention also comprises a set of face drive wheels for transmitting torque, comprising: the upper end surface transmission wheel is provided with an upper transmission wheel surface with a part of texture; one or more double-sided intermediate end face drive wheels, each double-sided intermediate end face drive wheel having an at least partially textured intermediate drive wheel first face configured to engage the at least partially textured upper drive wheel face and on an opposite side of an at least partially textured intermediate drive wheel second face configured to engage an at least partially textured lower drive wheel face of a lower end face drive wheel to transmit torque from the upper end face drive wheel to the lower end face drive wheel. In one embodiment, the partially textured drive sheave face is a face gear in which a plurality of teeth extend from the outer edge of the drive sheave to the center of the drive sheave, the height, slope and spacing of the teeth being application specific.

One embodiment of the present invention includes a ratchet device. The ratchet device includes a handle extending from a ratchet head having a hollow interior, and a set of end face drive wheels disposed within the hollow interior. The set of end face transmission wheels comprises a set of one or more middle end face transmission wheels between the upper end face transmission wheel and the lower end face transmission wheel. The set of end face drive wheels includes an upper end face drive wheel having an upper end face drive wheel first face connected to the ratchet head, the upper end face drive wheel first face being located on an opposite side of the at least partially textured upper end face drive wheel second face, and one or more intermediate end face drive wheels. Each intermediate end face drive wheel has an at least partially textured intermediate end face drive wheel first face engaging at least a portion of the at least partially textured upper end face drive wheel second face and on an opposite side of the at least partially textured intermediate end face drive wheel second face. The lower end face drive wheel includes an at least partially textured lower end face drive wheel first face connected to and on an opposite side of at least a portion of the at least partially textured intermediate end face drive wheel second face. A socket interface is coupled to the second face of the lower end face drive wheel and is configured to extend from the hollow cavity to removably receive a socket, wherein torque is transferred from the ratchet head to the socket interface at different rotation ratios via the set of end face drive wheels.

One embodiment includes a set of face pulleys for transmitting torque having a set of double-sided intermediate face pulleys between an upper face pulley and a lower face pulley. The upper end surface transmission wheel is provided with an upper transmission wheel surface which is at least partially textured. One or more double-sided intermediate end face drive wheels each have an at least partially textured intermediate drive wheel first face configured to engage the at least partially textured upper drive wheel face and on an opposite side of the at least partially textured intermediate drive wheel second face configured to engage the at least partially textured lower drive wheel face of the lower end face drive wheel to transmit torque from the upper end face drive wheel to the lower end face drive wheel.

The invention also includes a method of manufacturing a torque-transmitting mechanism, comprising the steps of: positioning an at least partially textured upper drive wheel face of the upper drive wheel in contact with an at least partially textured intermediate drive wheel first face of the one or more double-sided intermediate drive wheels, and positioning an at least partially textured intermediate drive wheel second face of the one or more double-sided intermediate drive wheels in contact with an at least partially textured lower drive wheel face of the lower drive wheel to transmit torque from the upper drive wheel to the lower drive wheel.

Drawings

For a more complete understanding of the features and advantages of the present invention, reference is now made to the detailed description of the invention along with the accompanying figures in which:

FIG. 1 shows a perspective view of the ratchet wrench of the present invention;

FIGS. 2A-2C show side cross-sectional views of the ratchet wrench of the present invention;

FIG. 3A is an exploded view of the head of one embodiment of the wrench of the present invention;

fig. 3B is a side view of the second transmission wheel;

FIG. 3C is a top view of the second drive wheel housing;

FIG. 3D is a side view of one of the intermediate drive wheels;

FIG. 3E is a top view of the intermediate drive wheel housing;

FIG. 3F is a side view of the first drive wheel;

FIG. 3G is a top view of the first drive wheel housing;

FIG. 4 is a perspective view of one embodiment of the head of the ratchet wrench of the present invention;

FIGS. 5A and 5B are overlapping perspective views of the drive wheel of the present invention;

FIG. 6A is a top view and FIG. 6B is a perspective view of one embodiment of a housing of the secondary drive wheel of the present invention;

FIG. 6C is a perspective view of one embodiment of a secondary drive wheel of the present invention;

FIG. 6D is a side view of one embodiment of the secondary drive wheel and secondary drive wheel housing of the present invention;

FIG. 6E is a top view and FIG. 6F is a perspective view of one embodiment of the intermediate drive wheel housing of the present invention;

fig. 6G is a perspective view of the intermediate transmission wheel;

FIG. 6H is a side view of an intermediate drive wheel housing containing a plurality of intermediate drive wheels overlapping the second drive wheel housing and the second drive wheel;

FIG. 6I is a cross-sectional view of one embodiment of the drive wheel drive mechanism of the present invention;

FIG. 7 is a side view of one embodiment of a drive wheel arrangement of the present invention;

FIG. 8 is a side view of a double-sided drive wheel arrangement of one embodiment of the present invention;

FIG. 9A is a view of another embodiment of the present invention showing different drive wheels and overlap thereof;

FIG. 9B is a top view of the first drive wheel having a central portion thereof surrounded by a toothless region;

FIG. 9C is a top view of one of the intermediate drive wheels;

fig. 9D is a top view of the second transmission wheel;

FIG. 10 is a side view of another embodiment of the present invention in which one of the drive wheels is fixed;

FIG. 11A is a plan view showing another embodiment of the transmission wheel of the present invention, and FIGS. 11B and 11C are side views showing the transmission of the transmission wheel shown in FIG. 11A;

FIG. 11D shows a perspective view of a drive wheel transmission system;

FIG. 11E shows a top view of another embodiment of the drive wheel transmission of the present invention in use with a ratchet insert (similar to a splined insert);

FIG. 11F shows a top view of another embodiment of the drive wheel transmission of the present invention used in conjunction with a ratchet insert (similar to a splined insert);

12A, 12B and 12C show side views of a dual sided drive wheel transmission system;

13A-13E show perspective views of the drive wheel transmission system;

14A-14C are views of the drive wheel transmission system of FIG. 13, wherein the drive wheels are spaced apart in FIG. 14A, aligned with each other in FIG. 14B, and engaged in FIG. 14C;

15A and 15B illustrate the drive wheel transmission system of FIG. 14, which is suitable for use with a large coupling joint;

FIG. 16 is a view of the drive wheel drive system of the present invention positioned in a crowbar;

FIG. 17A is an exploded view of another embodiment of the present invention, specifically a wrench;

FIG. 17B is an exploded view of the wrench head including bolt holes for receiving bolts, nuts or other fasteners;

18A and 18B are exploded isometric views of the drive wheel transmission system of FIG. 14, which is suitable for use with larger construction joints;

FIG. 19 is an exploded isometric view of the gear system of FIG. 18, the system being adapted with a multiplier gear set;

FIG. 20A is an exploded isometric view of a gear system having multiple jaws and a single swing handle with a multiplier gear set;

FIG. 20B is an isometric view of a gear system having multiple jaws and a single swing handle with a multiplier gear set;

FIG. 21 is an exploded isometric view of a gear system having a multiplier gear set used as a drive extension structure;

FIG. 22 is an exploded isometric view of a gear system having a double multiplication gear set used as a drive extension;

FIGS. 23A-23D are isometric views of an articulated wrench including a handle connected to upper and lower hinges;

FIGS. 24A-24E are isometric views of components of the hinge wrench;

FIGS. 25A-25C are views of a telescoping rod used with a crowbar, support rod, or other implement disclosed herein;

26A, 26B, and 26C are views showing an end face drive wheel assembly with a reverse mechanism;

FIGS. 27A and 27B are views of a geared compression ratchet wrench;

fig. 28A and 28B are views of a gear drive type compression ratchet wrench having a pair of end face drive wheels.

Detailed Description

While the making and using of various embodiments of the present invention are described in detail below, it should be appreciated that the present invention provides many applicable inventive concepts which can be embodied in a wide variety of specific contexts. The specific embodiments discussed herein are merely illustrative of specific ways to make and use the invention, and do not delimit the scope of the invention.

To facilitate an understanding of the invention, a number of terms or phrases are defined below. Terms or phrases defined herein have meanings as commonly understood by one of ordinary skill in the art to which this invention pertains. The terms "a" and "the" do not refer to their singular form only, but include the entire class of which an example is given for purposes of illustration. The terminology herein is used to describe specific embodiments of the invention, but its use is not intended to limit the scope of the invention, except as set forth in the claims.

The invention comprises a set of face drive wheels for transmitting torque. The set of drive wheels includes an upper face drive wheel having an at least partially textured upper drive wheel face and one or more double-sided intermediate face drive wheels, each double-sided intermediate face drive wheel including an at least partially textured intermediate drive wheel first face configured to engage the at least partially textured upper drive wheel face and located on an opposite side of an at least partially textured intermediate drive wheel second face configured to engage an at least partially textured lower drive wheel face of the lower face drive wheel to transmit torque from the upper face drive wheel to the lower face drive wheel.

FIG. 1 is a perspective view of one embodiment of the ratchet wrench 10 of the present invention. The ratchet wrench 10 includes a body 12 including a head portion 14 and a handle portion 16 extending from the head portion 14. The handle portion 16 is configured to be grasped by a user of the wrench 10. The head 14 houses a drive mechanism 18 (described in detail below) in a drive wheel cavity (not shown) formed in a body back side 20 of the ratchet wrench 10. The body back side 20 includes a reverse 22 that is operated by a knob 24 on the body back side 20 to selectively engage the directional movement of the transmission 18. The head 14 includes a sleeve engagement portion 26 on a front face 28 opposite the body back side 20. A drive wheel cavity (not shown) is located between the front face 28, the body back side 20 and the side of the head 14. The drive wheel cavity (not shown) may be closed or open and may be formed in the head 14, body back side 20, front face 28, or a portion thereof.

The sleeve engaging portion 26 includes a cylindrical recess 30 for receiving a spring (not shown) and a ball 32. The cylindrical recess 30, the spring (not shown) and the ball 32 are configured such that a portion of the ball 32 and the spring (not shown) are retained within the cylindrical recess 30, while the spring (not shown) biases another portion of the ball 32 out of the cylindrical recess 30. This allows the ball 32 to be pushed substantially into the cylindrical recess 30 while the sleeve (not shown) is being attached to the sleeve engagement portion 26, but still presses against the sleeve (not shown) so that the sleeve (not shown) remains attached to the sleeve engagement portion 26. To remove the sleeve (not shown), the user simply pulls the sleeve (not shown) away from the front face 28. The ball 32 is allowed to rotate thereby allowing the sleeve (not shown) to be removed. Of course, other arrangements may be used to retain a sleeve (not shown) to the sleeve engagement 26, and the illustrated embodiment should not be considered in any limiting sense.

Fig. 2A-2C show side cross-sectional views of the ratchet wrench 10 of the present invention. FIG. 2A is a cross-sectional view of one embodiment of the ratchet wrench 10 of the present invention. The ratchet wrench 10 includes a body 12 having a head portion 14 and a handle portion 16 connected by a rod 34. The handle portion 16 is configured to be grasped by a user of the wrench 10 and may include a textured area 36. Head 14 includes a body back side 20 having an inversion member 22 with a knob 24 provided on body back side 20. The head 14 has a socket engaging portion 26 at a front face 28 opposite the body back side 20 to form a drive wheel cavity 48. The sleeve engaging portion 26 includes a cylindrical recess 30 for receiving a spring 38 and a ball 32. The cylindrical recess 30, the spring 38, and the ball 32 are configured such that a portion of the ball 32 and the spring 38 are retained in the cylindrical recess 30, while the spring 38 biases another portion of the ball 32 out of the cylindrical recess 30. This allows the ball 32 to be pushed substantially into the cylindrical recess 30 while the sleeve (not shown) is being attached to the sleeve engagement portion 26, but still be able to compress the sleeve (not shown) so that the sleeve (not shown) remains attached to the sleeve engagement portion 26. To remove the sleeve (not shown), the user simply pulls the sleeve (not shown) away from the front face 28. The ball 32 is allowed to rotate, thereby allowing the user to more easily move the sleeve (not shown). Of course, other structural configurations may be used to retain a sleeve (not shown) to the sleeve engagement portion 26, and the illustrated embodiment should not be considered in any limiting sense.

The head 14 houses a drive mechanism 18 that is disposed between the body back side 20 and the front face 28 of the ratchet wrench 10. In one embodiment, the transmission mechanism 18 includes a sleeve engagement portion 26 that includes a first drive wheel 40. The first drive wheel 40 has a first drive wheel face (not shown) facing away from the sleeve engagement portion 26. The intermediate drive wheel housing 42 includes a plurality of

intermediate drive wheels

44a, 44b and 44c which pass through the intermediate drive wheel housing 42 and extend from the first drive wheel 40 to the second drive wheel 46. Each

intermediate transmission wheel

44a, 44b, 44c comprises an intermediate transmission wheel first face (not shown) arranged towards the first transmission wheel 40 and an intermediate transmission wheel second face (not shown) arranged towards the second transmission wheel 46. At least a portion of the intermediate drive wheel first face (not shown) contacts at least a portion of the first drive wheel face (not shown) and at least a portion of the intermediate drive wheel second face (not shown) contacts at least a portion of the second drive wheel face (not shown).

The direction of rotation of the second drive wheel 46 can be locked by means of the knob 24 on the body back side 20. The knob 24 adjusts the reversing element 22 to position a pawl (not shown) to limit the direction of rotation of the second drive wheel 46.

In operation, the second drive wheel 46 rotates in one direction depending on the position of the knob 24 and pawl (not shown). This configuration allows the handle portion 16 of the ratchet wrench 10 to smoothly rotate in one direction about the head portion 14. Rotation of the handle portion 16 of the ratchet wrench 10 in the opposite direction about the head portion 14 forces the parts to interlock and block rotation to force rotation of the second drive wheel 46. The direction of rotation can be reversed by moving the knob 24 which in turn moves the reversing element 22 to position the pawl (not shown) to limit the direction of rotation. The handle portion 16 of the ratchet wrench 10 is then free to rotate in the opposite direction, while rotation in the other direction causes these components to lock and prevent rotation thereof to force the second drive wheel 26 to rotate. This configuration allows the selective handle portion 16 to freely rotate clockwise while counterclockwise rotation of the handle portion 16 results in counterclockwise rotation of the sleeve engagement portion 26, or the configuration allows the selective handle portion 16 to rotate counterclockwise while clockwise rotation of the handle portion 16 results in clockwise rotation of the sleeve engagement portion 26.

In operation, rotation of the handle 12 causes rotation of the second drive wheel 46. At least a portion of the second gear face (not shown) contacts at least a portion of the second face (not shown) of each intermediate drive wheel. As the second drive wheel 46 rotates, the intermediate drive wheel second face (not shown) contacts the

intermediate drive wheels

44a, 44b and 44c, causing rotation. The

intermediate drive wheels

44a, 44b and 44c are positioned in the intermediate drive wheel housing 42 and are held in a vertical position and a horizontal position relative to the other components. As the

intermediate drive wheels

44a, 44b and 44c rotate, at least a portion of the intermediate drive wheel first face (not shown) contacts at least a portion of the first drive wheel face (not shown), thereby rotating the first drive wheel 40 and in turn rotating the socket joint 26.

Fig. 2B is a cross-sectional view of one embodiment of the ratchet wrench 10 of the present invention. The ratchet wrench 10 includes a body 12 including a head portion 14 and a handle portion 16. The head 14 includes a body back side 20 and a sleeve engaging portion 26 at a front face 28 opposite the body back side 20, thereby defining a drive wheel cavity 48. The socket engagement portion 26 includes a cylindrical recess (not shown) for receiving a spring (not shown) and a ball 32. The head 14 contains a drive mechanism 18 that is disposed between the body back side 20 and the front face 28 of the ratchet wrench 10. In one embodiment, the transmission mechanism 18 includes a sleeve engagement portion 26 that includes a first drive wheel 40. The first drive wheel 40 has a first drive wheel face (not shown) facing away from the sleeve engagement portion 26.

Intermediate drive wheels

44a and 44b extend from the first drive wheel 40 to a second drive wheel 46. Each

intermediate transmission wheel

44a, 44b comprises an intermediate transmission wheel first face (not shown) arranged towards the first transmission wheel 40 and an intermediate transmission wheel second face (not shown) arranged towards the second transmission wheel 46. At least a portion of the intermediate drive wheel first face (not shown) contacts at least a portion of the first drive wheel face (not shown) and at least a portion of the intermediate drive wheel second face (not shown) contacts at least a portion of the second drive wheel face (not shown).

Fig. 2C is a cross-sectional view of one embodiment of the ratchet wrench 10 of the present invention. The ratchet wrench 10 includes a body 12 including a head portion 14 and a handle portion 16. Head 14 includes a body back side 20 and a sleeve engaging portion 26 at a front face 28 opposite body back side 20, thereby defining a drive wheel cavity 48. The socket engagement portion 26 includes a cylindrical recess (not shown) for receiving a spring (not shown) and a ball 32. The head 14 contains a drive mechanism 18 that is disposed between the body back side 20 and the front face 28 of the ratchet wrench 10. In one embodiment, the transmission mechanism 18 includes a sleeve engagement portion 26 that includes a first drive wheel 40. The first drive wheel 40 has a first drive wheel face (not shown) facing away from the sleeve engagement portion 26.

Intermediate drive wheels

intermediate transmission wheel

Fig. 3A is an exploded view of the head 14 of one embodiment of the ratchet wrench 10 of the present invention. The ratchet wrench 10 includes a body 12 having a head portion 14 and a handle portion 16 connected by a rod 34. The handle portion 16 is configured to be grasped by a user of the wrench 10. The head 14 contains a drive mechanism 18 located in a drive wheel cavity 48 between the body back side 20 and the front face 28. The body back side 20 includes a reverse piece (not shown) having a knob (not shown) on the body back side 20. Body back side 20 includes a fastening opening 50a sized to receive retaining

fasteners

52a and 52b for securing drive mechanism 18 within drive wheel cavity 48 of head 14.

The second drive wheel 46 is positioned in a second drive wheel housing opening 54 of a second drive wheel housing 56 that is configured to fit into the drive wheel cavity 48. The second drive wheel housing 56 includes

fastening openings

50a, 50b which are aligned with and securable by the

positioning fasteners

52a and 52 b. The second drive wheel 46 has a second drive wheel face 58 that can apply torque to an engagement surface. The second gear surface 58 may be a ribbed surface, a textured surface, a wavy surface, a slanted striated surface, a textured surface, a grooved surface, a meshed surface, a toothed surface, a peened surface, a splined surface, a smooth surface, a roughened surface, a sticky surface or other surface suitable for allowing friction between the surfaces. The second drive wheel 46 includes a second drive wheel back 60 opposite the second drive wheel face 58 and a second drive wheel side 62 located between the second drive wheel back 60 and the second drive wheel face 58. The second drive wheel face 58, the second drive wheel back face 60, and/or the second drive wheel side face 62 can be configured to selectively limit rotation of the second drive wheel 46 and thereby engage the ratchet mechanism.

The intermediate drive wheel housing 42 is disposed adjacent the second gear housing 56 such that a portion of the intermediate drive

wheel housing openings

64a, 64b, 64c and 64d overlap the second drive wheel housing opening 54 and the second gear 46. Each intermediate drive

wheel housing opening

64a, 64b, 64c and 64d receives a corresponding

intermediate drive wheel

44a, 44b, 44c and 44 d. Each

intermediate drive wheel

44a, 44b, 44c and 44d has an intermediate drive wheel first face 66 and an intermediate drive wheel second face 68, which can each be ribbed, textured, undulating, slanted striped, ruled, grooved, meshed, toothed, peened, splined, smooth, roughened, sticky or other suitable surface that allows friction between the surfaces. The

intermediate drive wheels

44a, 44b, 44c and 44d are positioned such that a portion of the second face 68 of each intermediate drive wheel aligns with and matches the second gear face 58 of the second drive wheel 46.

The first drive wheel 40 is positioned in a first drive wheel housing opening 70 of a first drive wheel housing 72 having

fastening openings

50a and 50 b. The first drive wheel 40 includes a sleeve engaging portion 26 that extends to engage a sleeve (not shown) or elongate structure (not shown). The socket engagement portion 26 includes a cylindrical recess (not shown) for receiving a spring (not shown) and a ball 32. The cylindrical recess (not shown), the spring (not shown), and the ball 32 are configured such that a portion of the ball 32 and the spring (not shown) are retained in the cylindrical recess (not shown), while the spring (not shown) biases another portion of the ball 32 out of the cylindrical recess (not shown). This allows the ball 32 to be pushed substantially into the cylindrical recess (not shown) while the sleeve (not shown) is being secured over the sleeve engagement 26, but still apply pressure to the sleeve so that the sleeve (not shown) remains attached to the sleeve engagement 26. To remove the sleeve (not shown), the user simply pulls the sleeve (not shown) away from the front face 28. The ball 32 is allowed to rotate, whereby it is easier for the user to move the sleeve. Of course, other structural configurations may be used to retain the sleeve (not shown) to the sleeve engagement portion 26. The first drive wheel 40 includes a first drive wheel face 74 opposite the sleeve-engaging portion 26 and includes a surface that is ribbed, textured, undulating, slanted-striped, ruled, grooved, meshed, toothed, peened, splined, smooth, roughened, sticky or other suitable surface that allows friction between the surfaces. The first drive wheel housing opening 70 is configured to seat at least a portion of the first drive wheel face 74 in contact with a portion of the intermediate drive wheel first face 66. The first drive wheel housing 72 includes

fastening openings

50a and 50b that are aligned with and can be fastened with the

positioning fasteners

52a and 52 b.

The front face 28 is positioned on an opposite face of the body back side 20 to secure the drive mechanism 18 in the drive wheel cavity 48 of the ratchet wrench 10. The

positioning fasteners

52a and 52b are disposed through the

fastening openings

50a and 50b in the second drive wheel housing 56, the intermediate drive wheel housing 42 and the first drive wheel housing 72 and into the fastening openings 76a and 76b to allow the front face 28 to close the drive wheel cavity 48 and secure the drive mechanism 18 in the drive wheel cavity 48 of the head 14.

Fig. 3B is a side view of the second transmission wheel 46. The second drive wheel 46 includes a second drive wheel back 60 opposite the second drive wheel face 58 and a second drive wheel side 62 between the second drive wheel back 60 and the second drive wheel face 58. The second drive wheel face 58, second drive wheel back face 60, and/or second drive wheel side face 62 can be ribbed, textured, wavy, undulating, slanted, linear, grooved, intermeshing, toothed, shot-peened, splined, smooth, roughened, tacky, or other suitable surfaces that allow friction between the surfaces.

Fig. 3C is a plan view of the second transmission wheel housing 56. The second drive wheel 46 is positioned in a second drive wheel housing opening 54 of a second drive wheel housing 56 that is configured to fit into a drive wheel cavity (not shown) and that can be secured by engaging the

fastening openings

50a and 50 b. The secondary drive wheel surface 58 may be a ribbed surface, a textured surface, a wavy surface, a corrugated surface, a slanted strip surface, a linear surface, a grooved surface, a meshed surface, a toothed surface, a peened surface, a splined surface, a smooth surface, a roughened surface, a sticky surface, or any other surface suitable for allowing friction between surfaces.

Fig. 3D is a side view of one of the intermediate transmission wheels 44. Each intermediate drive wheel 44 has an intermediate drive wheel first face 66 separated from an intermediate drive wheel second face 68 by a drive wheel intermediate portion. The intermediate drive wheel first face 66, the intermediate drive wheel second face 68, and/or the drive wheel middle portion can each be a ribbed face, a textured face, a wavy face, a knurled face, a slanted striped face, a textured face, a grooved face, a meshed face, a toothed face, a peened face, a splined face, a smooth face, a rough face, a sticky face, or other suitable surface that allows friction between the surfaces.

Fig. 3E is a top view of the intermediate drive wheel housing 42. The intermediate drive wheel housing 42 includes a plurality of intermediate drive

wheel housing openings

64a, 64b, 64c and 64d which overlap a second drive wheel housing opening (not shown), a second drive wheel (not shown) and which are secured with the

fastening openings

50a and 50 b. Each intermediate drive

wheel housing opening

64a, 64b, 64c, 64d receives a corresponding

intermediate drive wheel

44a, 44b, 44c, 44d having an intermediate drive wheel

first face

66a, 66b, 66c, 66d which may be a ribbed face, a textured face, a wavy face, a ridged face, a slanted striped face, a textured face, a grooved face, a toothed face, a peened face, a splined face, a smooth face, a rough face, a sticky face or other suitable surface that allows friction between the surfaces.

Fig. 3F is a side view of one of the first drive wheels 40. The first drive wheel 40 includes a sleeve engaging portion 26 that extends to engage a sleeve (not shown) or elongate structure (not shown). The socket engagement portion 26 includes a cylindrical recess (not shown) for receiving a spring (not shown) and a ball 32. The first drive wheel 40 includes a first drive wheel face 74 opposite the sleeve engagement portion 26 and includes a surface that is ribbed, textured, undulating, slanted ribbed, linear, grooved, meshed, toothed, peened, splined, smooth, roughened, sticky or other suitable surface that allows friction between the surfaces.

Fig. 3G is a top view of the first drive wheel housing 72. The first drive wheel 40 is positioned in a first drive wheel housing opening 70 of a first drive wheel housing 72 having

fastening openings

50a, 50 b. The first drive wheel 40 includes a sleeve engaging portion 26 that extends to engage a sleeve or elongate structure (not shown). The socket engaging portion 26 has a cylindrical recess (not shown) for receiving a spring (not shown) and a ball 32.

Fig. 4 is a perspective view of one embodiment of the head 14 of the ratchet wrench of the present invention. The ratchet wrench 10 includes a body (not shown) including a head portion 14 and a handle portion (not shown) extending from the head portion 14. The head 14 contains the drive mechanism 18 in a drive wheel cavity 48 between a back side of the body (not shown) and the front face 28 having

fastening openings

50a and 50b sized to receive a retaining fastener (not shown) to fasten the drive mechanism 18 in the drive wheel cavity 48 of the head 14.

The head 14 includes a socket joint 26 at a front face 28 opposite a body back side (not shown). The socket engagement portion 26 includes a cylindrical recess 30 (not shown) for receiving a spring (not shown) and a ball 32. The cylindrical recess 30, spring (not shown) and ball 32 are configured such that a portion of the ball 32 and the spring (not shown) are retained in the cylindrical recess 30, while the spring (not shown) biases another portion of the ball 32 out of the cylindrical recess 30. This allows the ball 32 to be pushed substantially into the cylindrical recess 30 while the sleeve (not shown) is being installed onto the sleeve engagement portion 26, but still presses on the sleeve so that the sleeve (not shown) remains attached to the sleeve engagement portion 26.

As can be seen from the figures, the outer contours of the first drive wheel housing opening 70 and the first drive wheel 40 are aligned with a portion of the

intermediate drive wheels

44a, 44b, 44c, 44d, thereby covering a portion of each

intermediate drive wheel

44a, 44b, 44c, 44 d. The first drive wheel 40 has a first drive wheel face (not shown) that contacts an intermediate drive wheel first face (not shown) and an intermediate drive wheel second face (not shown) that contacts a second drive wheel face (not shown). In operation, a rotation wrench (not shown) rotates a second drive wheel (not shown) which in turn rotates each

intermediate drive wheel

44a, 44b, 44c, 44d via interaction between the second drive wheel face (not shown) and the intermediate drive wheel second face (not shown). As the intermediate drive wheel face (not shown) rotates, the corresponding intermediate drive wheel first face (not shown) rotates and in turn rotates the first drive wheel face (not shown), the first drive wheel 40 and the socket interface 26.

The first drive wheel 40 is positioned in a first drive wheel housing opening 70 of a first drive wheel housing (not shown) having

fastening openings

50a and 50b and located adjacent the front face 28. The first drive wheel housing (not shown), the intermediate drive wheel housing (not shown) and the second drive wheel housing (not shown) are all aligned by the size of the drive wheel cavity 48 and the location of the

fastening openings

50a and 50 b. This alignment allows partial overlap of the first drive wheel 40 and the

intermediate drive wheels

44a, 44b, 44c and 44d and the second drive wheel (not shown), resulting in specific gear ratios, e.g., 1:1, 1:2, 1:3, 1:4, 1:5, 1:6, 1:7, 1:8, 1:9, 1:10, 1:11, 1:12, 1:13, 1:14, 1:15, 1:16, 1:17, 1:18, 1:19, 1:20, 1:20, >20:1, 19:1, 18:1, 17:1, 16:1, 15:1, 14:1, 13:1, 12:1, 11:1, 10:1, 9:1, 8:1, 7:1, 6:1, 5:1, 4:1, 3:1, 2:1, 0.5:1, 0.25:1, 0.3:1, 0.1:1, 0.05:1, 0.25:0.6, and other variations and incremental ratios thereof.

FIG. 5A is an exploded perspective view of the overlap of the transmission of the present invention. The present invention provides for partial overlap of the second pulley 46 and the

intermediate pulleys

44a, 44b, 44c and 44d, and these intermediate transmission wheels partially overlap the first transmission wheel 40, thereby providing a certain transmission ratio, for example, 1:1, 1:2, 1:3, 1:4, 1:5, 1:6, 1:7, 1:8, 1:9, 1:10, 1:11, 1:12, 1:13, 1:14, 1:15, 1:16, 1:17, 1:18, 1:19, 1:20, 1:20, >20:1, 19:1, 18:1, 17:1, 16:1, 15:1, 14:1, 13:1, 12:1, 11:1, 10:1, 9:1, 8:1, 7:1, 6:1, 5:1, 4:1, 3:1, 2:1, 0.5:1, 0.25:1, 0.3:1, 0.1:1, 0.05:1, 0.25:0.6, and other variations and incremental ratios thereof.

The second drive wheel 46 includes a second drive wheel back surface 60 on an opposite side of the second drive wheel face 58 and a second drive wheel side surface 62 between the second drive wheel back surface 60 and the second drive wheel face 58. The second drive wheel face 58, the second drive wheel back face 60, and/or the second drive wheel side face 62 can be ribbed, textured, wavy, undulating, slanted, linear, grooved, intermeshing, toothed, shot-peened, splined, smooth, roughened, tacky, or other suitable surfaces that allow friction between the surfaces.

Each

intermediate drive wheel

44a, 44b, 44c and 44d has an intermediate drive wheel

first face

66a, 66b, 66c and 66d and an intermediate drive wheel

second face

68a, 68b, 68c and 68d, which may independently be ribbed, textured, wavy, undulating, slanted striped, textured, grooved, interlocking, toothed, peened, splined, smooth, roughened, adhesive, or other suitable surface that allows friction between surfaces.

The first drive wheel 40 includes a first drive wheel face 74 opposite the first drive wheel back face 76 and includes a surface that is ribbed, textured, wavy, undulating, slanted striped, textured, grooved, meshed, toothed, peened, splined, smooth, roughened, sticky or other suitable surface that allows friction between the surfaces.

FIG. 5B is a perspective view of an overlapping condition of the transmission assembly of the present invention. This figure shows one possible alignment of the drive wheels of the present invention with an overlap of 35-75%. The second drive wheel 46 includes a second drive wheel back face 60 on the opposite side of the second drive wheel face 58, in which case approximately half of the second drive wheel face 58 overlaps approximately half of each intermediate drive wheel

second face

68a, 68b, 68c and 68 d. This overlap allows the second pulley 46 to rotate and drive the

intermediate pulleys

44a, 44b, 44c and 44d in rotation, with the size, face and number of teeth of each pulley and the pitch and wheel size on the pulleys determining the transmission ratio. The intermediate drive wheel second faces 68a, 68b, 68c and 68d are connected to the intermediate drive wheel first faces 66a, 66b, 66c and 66d such that as the intermediate drive wheel second faces 68a, 68b, 68c and 68d rotate, the intermediate drive wheel first faces 66a, 66b, 66c and 66d are also rotated. The intermediate drive wheel first faces 66a, 66b, 66c and 66d overlap about half of the first drive wheel face 74 of the first drive wheel 40. As the intermediate drive wheel first faces 66a, 66b, 66c and 66d rotate, contact with the first drive wheel face 74 causes the first drive wheel face to rotate and in turn rotate the first drive wheel 40. In addition, the overlap in turn allows the second pulley 46 to rotate and drive the

intermediate pulleys

44a, 44b, 44c and 44d to rotate, with the tooth size, face and number of teeth on each pulley and the pitch and wheel size on the pulleys determining the gear ratio. The

intermediate gearwheels

44a, 44b, 44c and 44d rotate the first gearwheel 40, wherein the size of the teeth on each gearwheel, the tooth flank, the number of teeth, the pitch of the teeth on the gearwheels and the size of the gearwheels determine the gear ratio. Rotation of the second pulley 46 causes rotation of the first pulley 40, with the tooth size, tooth face, tooth number on each pulley, the pitch on the pulleys and the pulley size of the

intermediate pulleys

44a, 44b, 44c, 44d determining the final drive ratio.

Fig. 6A is a plan view and fig. 6B is a perspective view of one embodiment of a case of the second transmission wheel of the present invention. A second drive wheel (not shown) may be positioned in the second drive wheel housing opening 54 of the second drive wheel housing 56. The second pulley housing 56 may be sized to fit within a pulley cavity (not shown). The second drive wheel housing face 76 may be a ribbed face, a textured face, a wavy face, an undulating face, a slanted strip face, a textured face, a grooved face, a meshing face, a toothed face, a peened face, a splined face, a smooth face, a rough face, a sticky face, or other suitable surface that allows friction between the surfaces.

Fig. 6C is a perspective view of one embodiment of the secondary drive wheel of the present invention. The second drive wheel 46 includes a second drive wheel back 60 opposite the second drive wheel face 58 and a second drive wheel side 62 located between the second drive wheel back 60 and the second drive wheel face 58. The second drive wheel face 58, the second drive wheel back face 60, and/or the second drive wheel side face 62 can be ribbed, textured, undulating, ribbed, striated, grooved, intermeshing, belt driven, shot blasted, splined, smooth, roughened, tacky, or any other suitable surface that allows friction between the surfaces.

Fig. 6D is a side view of one embodiment of the secondary drive wheel housing and secondary drive wheel of the present invention. The second drive wheel 46 can be positioned in a second drive wheel housing opening 54 of a second drive wheel housing 56. The second pulley housing 56 may be sized to fit within a pulley cavity (not shown). The second drive wheel 46 extends through a second drive wheel housing opening 54, which has exposed portions on either side of a second drive wheel housing 56. The second drive wheel 46 includes a second drive wheel back surface 60 opposite the second drive wheel face 58 and a second drive wheel side surface 62 located between the second drive wheel back surface 60 and the second drive wheel face 58. The second drive wheel face 58, the second drive wheel back face 60, and/or the second drive wheel side face 62 can be ribbed, textured, undulating, ribbed, striated, grooved, intermeshing, belt driven, shot blasted, splined, smooth, roughened, tacky, or any other suitable surface that allows friction between the surfaces.

Fig. 6E is a top view and fig. 6F is a perspective view of one embodiment of the intermediate drive wheel housing 42 of the present invention. The intermediate drive wheel housing 42 includes intermediate drive

wheel housing openings

64a, 64b, 64c and 64d which overlap the secondary drive wheel housing opening (not shown) and the secondary drive wheel. Each intermediate drive

wheel housing opening

64a, 64b, 64c and 64d receives a respective intermediate drive wheel 44 as shown in FIG. 6G. Each intermediate drive wheel 44 has an intermediate drive wheel first face 66 and an opposite intermediate drive wheel second face 68, the first and second faces being separated by an intermediate drive wheel side 78. The intermediate drive wheel 44 may have a plurality of faces that are independently ribbed, textured, undulating, slanted striped, textured, grooved, meshed, toothed, shot blasted, splined, smooth, rough, sticky or other suitable surface that allows friction between surfaces.

Fig. 6H is a side view of the intermediate drive wheel housing 42 having

intermediate drive wheels

44a, 44b, 44c positioned in

rack openings

64a, 64b, 64c that overlap with a second drive wheel housing opening (not shown) and a second drive wheel (not shown). Each intermediate drive

wheel housing opening

64a, 64b, 64c receives a respective

intermediate drive wheel

44a, 44b, 44 c. Each

intermediate transfer wheel

44a, 44b, 44c has an intermediate transfer wheel

first face

66a, 66b, 66c and an opposite intermediate transfer wheel

second face

68a, 68b, 68c, the first and second faces being separated by an intermediate transfer

wheel side face

78a, 78b, 78 c. The

intermediate drive wheels

44a, 44b, 44c may independently have ribbed, textured, undulating, slanted ribbed, ruled, grooved, meshed, toothed, peened, splined, smooth, rough, sticky or other suitable surfaces to allow friction to be generated between the intermediate drive wheel first faces 66a, 66b, 66c and the intermediate drive wheel second faces 68a, 68b, 68c and the surfaces on the intermediate drive wheel side faces 78a, 78b, 78 c.

Fig. 6I is a cross-sectional view of one embodiment of the transmission 18 of the present invention. Fig. 6I shows the intermediate drive wheel housing 42 with a plurality of intermediate drive wheels positioned between the two second

drive wheel housings

56a and 56b and the

second drive wheels

46a and 46 b. The intermediate drive wheel housing 42 includes three

intermediate drive wheels

44a, 44b and 44c positioned in drive

wheel housing openings

64a, 64b and 64c which partially overlap the secondary drive wheel housing opening 54 and the secondary drive wheel 46. Each intermediate drive

wheel housing opening

64a, 64b, 64c receives a respective

intermediate drive wheel

44a, 44b, 44 c. Each

intermediate transfer wheel

44a, 44b, 44c has an intermediate transfer wheel

first face

66a, 66b, 66c and an opposite intermediate transfer wheel

second face

68a, 68b, 68c separated by an intermediate

transfer wheel side

78a, 78b, 78 c. A portion of each intermediate drive wheel

first face

66a, 66b, 66c contacts a portion of the second drive wheel face 58a of the second drive wheel 46a located in the second drive wheel housing opening 54a of the second drive wheel housing 56 a. The intermediate drive wheel second faces 68a, 68b, 68c contact the second drive wheel face 58b of the second drive wheel 46b located in the second drive wheel housing opening 54b of the second drive wheel housing 56 b. The overlap allows the second pulley 46a to rotate and drive the

intermediate pulleys

44a, 44b and 44c to rotate, wherein the size of the teeth on each pulley, the face of the teeth, the number of teeth, the pitch on the pulleys and the size of the pulleys determine the gear ratio. As a result, the second transmission wheel 46a and the second transmission wheel 46b rotate according to the transmission ratio determined by the

intermediate transmission wheels

44a, 44b and 44 c.

Another embodiment of the drive mechanism of the present invention includes the use of inserts (e.g., pins, dowels, rods, spikes, posts, squares, numbs, tabs, dots, bumps, or other similar positioning mechanisms) to position the drive wheels of the present invention.

An intermediate drive wheel (not shown) may be positioned between two second drive wheel housings (not shown) and a second drive wheel (not shown) by a plurality of pins extending through the drive wheel housings. The three intermediate drive wheels (not shown) may be positioned by three pins (not shown) in a desired position to align the three intermediate drive wheels (not shown) partially overlapping the second drive wheel (not shown). Each of the three intermediate drive wheels (not shown) has an intermediate drive wheel first face (not shown), and an opposite intermediate drive wheel second face, separated by an intermediate drive wheel side face (not shown). A portion of the first face (not shown) of each intermediate drive wheel contacts a portion of the second drive wheel face (not shown) of the second drive wheel (not shown) positioned with the pin (not shown). The intermediate drive wheel second face (not shown) contacts a second drive wheel face (not shown) of a second drive wheel (not shown). This overlap allows the second pulley (not shown) to rotate and drive the intermediate pulley (not shown) to rotate, wherein the size of the teeth on each pulley, the face of the teeth, the number of teeth, the pitch on the pulley and the size of the wheels determine the transmission ratio. As a result, the second drive wheel (not shown) rotates according to the transmission ratio determined by the intermediate drive wheel (not shown).

The skilled person will appreciate that the shape of the carrier, the thickness of the carrier, the position of the openings, the number of openings, the alignment of the openings, the alignment of these openings relative to the other openings may vary depending on the specific application or desired gear ratio. For illustrative purposes, some of the various embodiments of the shape, number and location of the openings of the drive wheel housing are described below.

The drive wheel housing may be generally circular and have five generally circular drive wheel housing openings. The drive wheel housing includes a cutout therein. The drive wheel housing openings receive a first set of drive wheels positioned in overlapping relation with a second set of drive wheels (not shown) such that rotation of the first set of drive wheels rotates the second set of drive wheels (not shown) at a drive ratio determined by the drive wheel size and the drive wheel surface.

The drive wheel housing may be generally circular and have two generally circular drive wheel housing openings. The drive wheel housing openings receive a first set of drive wheels positioned in overlapping relation with a second set of drive wheels such that rotation of the first set of drive wheels rotates the second set of drive wheels at a drive ratio determined by the drive wheel size and the drive wheel surface.

The drive wheel housing may be generally circular and have a generally rectangular drive wheel housing opening. The drive wheel housing opening receives a first set of drive wheels positioned in overlapping relation with a second set of drive wheels such that rotation of the first set of drive wheels rotates the second set of drive wheels at a drive ratio determined by the drive wheel size and the drive wheel surface.

The drive wheel housing may be generally polygonal and have six generally circular drive wheel housing openings. The drive wheel housing opening receives a first set of drive wheels positioned in overlapping relation with a second set of drive wheels such that rotation of the first set of drive wheels rotates the second set of drive wheels at a drive ratio determined by the drive wheel size and the drive wheel surface.

The drive wheel housing may be generally rectangular and have four generally circular drive wheel housing openings. The drive wheel housing opening receives a first set of drive wheels (not shown) positioned in overlapping relation with a second set of drive wheels (not shown) such that rotation of the first set of drive wheels (not shown) rotates the second set of drive wheels (not shown) at a drive ratio determined by the drive wheel size and the drive wheel surface.

The drive wheel housing may be generally oval and have three generally circular drive wheel housing openings. The drive wheel housing opening receives a first set of drive wheels (not shown) positioned in overlapping relation with a second set of drive wheels (not shown) such that rotation of the first set of drive wheels (not shown) rotates the second set of drive wheels (not shown) at a drive ratio determined by the drive wheel size and the drive wheel surface.

The drive wheel housing may be generally triangular and have two generally oval drive wheel housing openings. The drive wheel housing opening receives a first set of drive wheels (not shown) positioned in overlapping relation with a second set of drive wheels (not shown) such that rotation of the first set of drive wheels (not shown) causes rotation of the second set of drive wheels (not shown) at a drive ratio determined by the drive wheel size and the drive wheel surface.

The drive wheel housing may be generally polygonal and have two generally circular drive wheel housing openings. The drive wheel housing opening receives a first set of drive wheels (not shown) positioned in overlapping relation with a second set of drive wheels (not shown) such that rotation of the first set of drive wheels (not shown) causes rotation of the second set of drive wheels (not shown) at a drive ratio determined by the drive wheel size and the drive wheel surface.

The skilled artisan will recognize that the shape of the shelf, the thickness of the shelf, the location of the openings, the number of openings, the alignment of the openings, and the alignment of the openings relative to the other openings can vary.

The drive wheel housing includes a drive wheel housing top surface and a drive wheel housing bottom surface 88 separated by a drive wheel housing side surface. The drive wheel housing includes drive wheel housing openings that extend from the drive wheel housing top surface to the drive wheel housing bottom surface. The drive wheel housing opening includes an opening sidewall and an opening edge extending around the opening on the housing bottom surface. The drive wheel may be positioned in a drive wheel housing opening of the drive wheel housing. The drive wheel includes a drive wheel back surface on an opposite side of the drive wheel face separated by drive wheel side surfaces. The edge of the drive wheel matching the edge of the opening is positioned around the periphery of the side of the drive wheel. In an alternative embodiment, the drive wheel rim and/or the opening rim itself is a ribbed surface, a textured surface, a wavy surface, an undulating surface, a slanted strip surface, a striated surface, a grooved surface, a meshed surface, a toothed surface, a peened surface, a splined surface, a smooth surface, a rough surface, a sticky surface or other suitable surface that allows friction between the surfaces. The drive wheel back surface may be in, above or below the surface of the drive wheel housing top surface. Similarly, the width of the drive wheel sides is sufficient to position the drive wheel faces in, above or below the surface of the drive wheel housing floor. The drive wheel face and/or the drive wheel back face may be ribbed, textured, wavy, undulating, angular, textured, grooved, meshed, toothed, shot blasted, splined, smooth, roughened, adhesive or any other suitable surface that allows friction between the surfaces. In another embodiment, the drive wheel face is stamped or formed on the back of the workpiece.

Fig. 7 is a side view of one embodiment of the drive wheel arrangement of the present invention. This embodiment of the invention comprises three

intermediate drive wheels

44a, 44b and 44c positioned in a partially overlapping manner with the second drive wheel 46 and the first drive wheel 40. The first drive wheel 40 includes a first drive wheel face 74 positioned toward the

intermediate drive wheels

44a, 44b and 44 c. Each

intermediate drive wheel

44a, 44b, 44c has an intermediate drive wheel

first face

66a, 66b, 66c which is located opposite the intermediate drive wheel

second face

68a, 68b, 68c and which are separated by an intermediate drive

wheel side face

78a, 78b, 78 c. The

intermediate drive wheels

44a, 44b, 44c may independently be ribbed, textured, undulating, slanted ribbed, textured, grooved, meshed, toothed, peened, splined, smooth, rough, sticky or other suitable surface that allows friction between surfaces. A portion of each intermediate drive wheel

first face

66a, 66b, 66c contacts a portion of the first drive wheel face 74 of the first drive wheel 40, the first drive wheel being positioned such that the overlapping

portions

106a, 106c of the first drive wheel faces contact and partially overlap the overlapping

portions

108a, 108c of the intermediate drive wheel first faces 66a, 66b, 66 c. A portion of each intermediate drive wheel

second face

68a, 68b, 68c contacts a portion of the second drive wheel face 58 of the second drive wheel 46, the second drive wheel being positioned such that the overlapping

portions

110a, 110c of the second drive wheel faces contact and partially overlap the overlapping

portions

112a, 112c of the intermediate drive wheel second faces 68a, 68b, 68 c. This arrangement allows the first drive wheel 40, the second drive wheel 46 and/or the three

intermediate drive wheels

44a, 44b and 44c to be moved towards or away from adjacent drive wheels to engage or disengage the drive mechanism and/or to allow rotation. This movement may be accomplished by selective engagement/disengagement using a magnet mechanism, a switch mechanism, a push mechanism, a twist mechanism, or other mechanisms known to those skilled in the art.

Fig. 8 is a side view of a double-sided drive wheel arrangement of one embodiment of the present invention. This embodiment of the invention includes an overlap of the first drive wheel 40 in contact with a first set of

intermediate drive wheels

44a, 44b, 44c contacting a double-sided drive wheel 114 in contact with a second set of

intermediate drive wheels

44d, 44e, 44f which in turn contact a second drive wheel 46. The first drive wheel 40 includes a first drive wheel face 74 positioned in a partially overlapping manner with the

intermediate drive wheels

44a, 44b, 44 c. Each

intermediate drive wheel

44a, 44b, 44c has an intermediate drive wheel

first face

66a, 66b, 66c which is on the opposite side of the intermediate drive wheel

second face

68a, 68b, 68c and which are separated by an intermediate drive

wheel side face

78a, 78b, 78 c. A portion of each intermediate drive wheel

first face

66a, 66b, 66c contacts a portion of the first drive wheel face 74 of the first drive wheel 40. A portion of each intermediate transfer wheel

second face

68a, 68b, 68c contacts a portion of the double-sided transfer wheel first face 116 such that a partial overlap is formed between the intermediate transfer wheel

second face

68a, 68b, 68c and the double-sided transfer wheel first face 116 of the double-sided transfer wheel 114. The double-sided drive wheel 114 includes a double-sided drive wheel second face 118 that is opposite the double-sided drive wheel first face 116 and that is separated by a double-sided drive wheel side 120. The double-sided drive wheel second face 118 is positioned to overlap a portion of the

intermediate drive wheels

44d, 44e, 44 f. Each

intermediate transfer wheel

44d, 44e, 44f has an intermediate transfer wheel

first face

66d, 66e, 66f opposite the intermediate transfer wheel

second face

68d, 68e, 68f and separated by an intermediate transfer

wheel side face

78d, 78e, 78 f. A portion of each intermediate drive wheel

first face

66d, 66e, 66f contacts a portion of the double-sided drive wheel second face 118 of the double-sided drive wheel 114. A portion of each intermediate drive wheel

second face

68d, 68e, 68f contacts a portion of the second drive wheel face 58 of the second drive wheel 46 such that a partial overlap is formed between the intermediate drive wheel

second face

68d, 68e, 68f and the second drive wheel face 58.

This overlap allows rotation of the first drive wheel 40 to be transmitted to the first set of

intermediate drive wheels

44a, 44b, 44c at a particular drive ratio defined by the drive wheel contact between the first drive wheel 40 and the first set of

intermediate drive wheels

44a, 44b, 44 c. The rotation of the first set of

intermediate transfer wheels

44a, 44b, 44c is imparted to the double-sided transfer wheel 114 at a specific transfer ratio defined by the transfer wheel contact between the first set of

intermediate transfer wheels

44a, 44b, 44c and the double-sided transfer wheel 114. The rotation of the double-sided drive wheel 114 is transferred to the second set of

intermediate drive wheels

44d, 44e, 44f at a specific gear ratio defined by the drive wheel contact between the double-sided drive wheel 114 and the second set of

intermediate drive wheels

44d, 44e, 44 f. The rotation of the second set of

intermediate drive wheels

44d, 44e, 44f is transmitted to the second drive wheel 46 at a specific gear ratio defined by the drive wheel contact between the second set of

intermediate drive wheels

44d, 44e, 44f and the second drive wheel 46. This mechanism allows the transmission ratio to be adjusted to the ratio desired for a particular application by adjusting the first set of

intermediate drive wheels

44a, 44b, 44c, the second set of

intermediate drive wheels

44d, 44e, 44f, the first drive wheel 40, the double-sided drive wheel 114 and/or the second drive wheel 46.

Although the present invention is discussed in connection with a hand tool, the drive wheel and drive mechanism of the present invention can be used in any device that employs a drive wheel. For example, the transmission wheel speed reduction and increasing device of the present invention may be used in automobiles, motorcycles, buses, trucks, trains, airplanes, boats, ships, watercraft, bicycles, carts, golf carts, dollies, sight-seeing cars, transmissions, linkages, gearboxes, differentials, overdrive, drive shafts, and other components having gears. Furthermore, the drive wheel speed reduction and increase apparatus of the present invention can be used in any apparatus that employs drive gears, including mechanical devices, turbines, air mills, water mills, pulleys, winches, wrenches, harnesses, manipulators, prostheses, toys, lawn mowers, elevators, escalators, rods and reels, screwdrivers, drilling tools, saws, construction equipment, hoisting machinery, compressors, crown blocks, grinders, winches, watches, copiers, wrenches, tie tools, wrench heads, ratchet wrenches, socket wrenches, right angle connections for drilling tools and other tools, bevel connections (0-90 °) for drilling tools and other tools, and other apparatus having gears. Furthermore, the drive wheel speed reduction and increase arrangement of the present invention may include a spline type gear drive mechanism (as described herein) for providing drive wheel speed reduction, acceleration and/or increased strength in a single arrangement.

Furthermore, the present invention may be used with different head designs that allow for flipping, swiveling, pivoting, rotating, locking, or other movement to position the head in a desired position.

Fig. 9A is a view of another embodiment of the invention showing different drive wheels and drive wheel overlap. The second drive wheel 46 includes a second drive wheel back surface 60 on an opposite side of the second drive wheel surface 58 and a second drive wheel side surface 62 between the second drive wheel back surface (not shown) and the second drive wheel surface 58. The second drive sheave face 58 includes a second drive sheave tooth face 122 at a near-center portion of the second drive sheave face 58.

The plurality of intermediate drive wheels 44 are positioned in contact with the second drive wheel face 58. Although two

intermediate drive wheels

44a and 44b are shown here, those skilled in the art will appreciate that more or fewer intermediate drive wheels may be employed, for example 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or more. Each intermediate drive wheel 44 has an intermediate drive wheel first face 66 and an intermediate drive wheel second face 68, a portion of which may be textured to contact other surfaces (e.g., independently ribbed, textured, wavy, undulating, angular, striated, grooved, meshing, toothed, peened, knurled, smooth, roughened, sticky or other surfaces suitable for allowing friction between surfaces), and a portion of which does not contact the primary drive is smooth or textured at a different height than the primary drive (e.g., independently ribbed, textured, wavy, undulating, angular striated, meshing, toothed, peened, splined, smooth, roughened, sticky or other surfaces suitable for allowing friction between surfaces). The first drive wheel 40 is positioned opposite the intermediate drive wheel 44 and includes a first drive wheel back face (not shown) on an opposite side of the first drive wheel face 74 and a first drive wheel side face 102 between the first drive wheel back face (not shown) and the first drive wheel face 74. The first drive wheel face 74 includes a first drive wheel drive face 132 at a near-center portion of the first drive wheel face 74.

Fig. 9B is a top view of the first drive wheel 40 having a first drive wheel center portion 120 surrounded by a toothless region 122. The first drive wheel center 120 may be ribbed, textured, wavy, undulating, slanted striated, grooved, meshed, toothed, peened, splined, smooth, roughened, sticky or other suitable surface that allows friction between surfaces. The first drive wheel pitch 124 is the distance from the first tooth 126 to the second tooth 128 and is a particular distance that may be varied or varied for a given application. In the illustrated view, the first drive wheel center 120 has a plurality of teeth, but in other embodiments the first drive wheel center 120 may be ribbed, textured, wavy, undulating, slanted striped, textured, grooved, meshed, toothed, peened, splined, smooth, roughened, sticky or other suitable surface that allows for friction between surfaces, and may have different orientations. The portion of the first drive sheave surface 74 occupied by the first drive sheave center portion 120 will depend on the particular application and gear used. The first drive wheel center section 120 is aligned with a portion of the intermediate drive wheel (not shown), the degree of overlap will again depend on the particular application. The first drive wheel center section 120 and the toothless region 122 function to allow rotation of the gear of the present invention. The gear pitch may include a spline-type arrangement, as seen elsewhere in this application, for increasing the strength of the drive wheel and the amount of pressure or torque that the drive wheel can withstand

Fig. 9C is a top view of one of the intermediate drive wheels 44 having an intermediate drive wheel first face 66, an intermediate drive wheel second face (not shown), which may independently be a ribbed face, a textured face, a wavy face, a slanted striped face, a textured face, a grooved face, a meshed face, a toothed face, a peened face, a splined face, a smooth face, a rough face, a sticky face, or other suitable surface that allows friction between the surfaces. The intermediate drive wheel first face 66 has an intermediate drive wheel first belt tooth face 130 on the outer periphery to align with the first drive wheel center section 120 of the first drive wheel 40 in fig. 9B. The intermediate drive wheel first face 66 has a central toothless first face 132 in the intermediate drive wheel first toothed surface 130. The first intermediate drive wheel pitch 134 is the distance from the first intermediate tooth 136 to the second intermediate tooth 138 and is a particular distance that may be varied or varied depending on a given application. Similarly, the intermediate drive wheel second face (not shown) may have an intermediate drive wheel second toothed surface (not shown) around the outside so as to align with the second drive wheel center portion (not shown) of the first drive wheel 40. The intermediate drive wheel second face (not shown) also has a central toothless second face (not shown) in the intermediate drive wheel first toothed face (not shown). The intermediate drive wheel first face 66 and the intermediate drive wheel second face (not shown) may be aligned with the second drive wheel face (not shown) of the second drive wheel (not shown), although the intermediate drive wheel first face 66 and the intermediate drive wheel second face (not shown) do not necessarily have the same shape and drive wheel arrangement. The invention also includes a plurality of drive wheel faces positioned within each other to provide a plurality of second drive wheel contact points from a single first drive wheel.

Fig. 9D is a top view of the second drive wheel 46 showing the second drive wheel face 58 opposite the second drive wheel back face (not shown). The second drive sheave face 58 includes a second drive sheave tooth face 140 on a portion of the second drive sheave face 58 that is surrounded by an inner toothless region 142 and an outer toothless region 144. The dimensions of the inner toothless region 142, the outer toothless region 144, and the second pulley tooth face 140 may vary depending on the particular application. The second drive wheel tooth spacing 146 is the distance from the first tooth 148 to the second tooth 150 and is a particular distance that may vary or vary depending on a given application. Although the toothless regions 122, the toothless first faces 132, the central toothless second faces (not shown), the inner toothless regions 142, and the outer toothless regions 144 are shown as toothless, these regions may have meshing structures (e.g., ribbed, textured, wavy, undulating, angular, striated, textured, grooved, interlocking, toothed, shot-peened, splined, smooth, rough, sticky, or other suitable surfaces that allow friction between the surfaces), different orientations, or different textured surfaces to mesh with other drive wheel transmissions or surfaces.

In another embodiment, the transmission may be of the opposite configuration to that of fig. 9, in which the outer portions of the first and second drive wheels are toothless and the inner portions are toothed to mesh with the intermediate gearless central and outer toothed intermediate drive wheels. In another embodiment, the transmission mechanism may be a hybrid of the above embodiments, wherein the first transmission wheel is as shown in fig. 11 and the second transmission wheel has the opposite configuration.

Although the figures show a number of possible alignments of the gearwheels of the invention (e.g. approximately 10-95% overlap of the gearwheels), this is exemplary only, and the actual percentage overlap, spacing, size, number of teeth, size of teeth, tooth position, tooth height, tooth angle and other parameters may vary depending on the particular application.

Fig. 10 is a side view of another embodiment of the present invention in which one of the drive wheels is stationary. The second drive wheel 46 includes a second drive wheel back surface 60 on the opposite side of the second drive wheel surface 58. The second drive sheave face 58 includes a second drive sheave tooth face 122 on an interior portion of the second drive sheave face 58. The intermediate drive wheel 44 is positioned in contact with the second drive wheel face 58. Although two

intermediate drive wheels

44a and 44b are shown here, the skilled person will appreciate that more or fewer intermediate drive wheels may be employed. Each intermediate drive wheel 44 has an intermediate drive wheel first face 66 and an intermediate drive wheel second face 68, some of which may be textured for engagement with other surfaces (e.g., independently ribbed, textured, wavy, undulating, angular ribbed, textured, grooved, interlocking, toothed, peened, splined, smooth, rough, sticky or other surfaces suitable for allowing friction between surfaces). The first drive wheel 40 is disposed opposite the intermediate drive wheel 44 and includes a first drive wheel back face (not shown) located opposite the first drive wheel face 74. The first drive wheel face 74 includes a first drive wheel tooth face 132 that is aligned with the intermediate drive wheel first face 66 of the intermediate drive wheel 44.

The overlap of the drive wheels of the present invention provides drive ratios of drive wheel deceleration or acceleration that can be 1:1, 1:2, 1:3, 1:4, 1:5, 1:6, 1:7, 1:8, 1:9, 1:10, 1:11, 1:12, 1:13, 1:14, 1:15, 1:16, 1:17, 1:18, 1:19, 1:20, 1: >20, >20:1, 19:1, 18:1, 17:1, 16:1, 15:1, 14:1, 13:1, 12:1, 11:1, 10:1, 9:1, 8:1, 7:1, 6:1, 5:1, 4:1, 3:1, 2:1, 0.5:1, 0.25:1, 0.3:1, 0.1:1, 0.05:1, 0.25:0.6, and other incremental ratios and variations thereof. Those skilled in the art will recognize that various combinations of sets of drive wheels may be used to achieve a particular gear ratio and incorporate the sets of drive wheels of the present invention to best translate to a desired gear ratio.

The combination of the gearing teeth and the layout of the gearwheels allows the torque and speed to be varied between an input value and an output value. For example, the combination of the 8-tooth gearwheels 160a, 160b, 160c and the 40-tooth gearwheels 162a, 162b, 162c results in a significant reduction in the transmission ratio. For example, the final gear ratio between the 8-tooth drive wheel 160a and the 40-tooth drive wheel 162a is 125: 1. This is achieved by the combination of the 8-tooth wheel 160a driving the 40-tooth wheel 162b at a ratio of 5:1, the 8-tooth wheel 160b driving the 40-tooth wheel 162c at a ratio of 5:1, and the 8-tooth wheel 160c driving the 40-tooth wheel 162a at a ratio of 5:1, so that the 100rpm input is converted to a 0.8rpm output (this conversion can also be achieved to convert a 0.8rpm input to a 100rpm output). For example, a 40-tooth drive pulley 162 is coupled to an 8-tooth drive pulley 160 to provide a 1:5 ratio, such that, depending on the speed of the main pulley 162 being 1rpm, the speed of the drive pulley 160 is 5 rpm. The 20-tooth drive wheel 164 and the 24-tooth drive wheel 166 are connected to the 40-tooth primary drive wheel 162 to provide a gear ratio of 1:2 and 1:1.66, respectively, so that the drive wheel 164 and the drive wheel 166 rotate at 2rpm and 1.66rpm, respectively, depending on the speed of the drive gear 162 being 1 rpm. For example, an 8-tooth final drive wheel 160 is connected to a 40-tooth drive wheel 162, resulting in a 5:1 ratio, with the drive wheel 162 rotating at 1rpm, depending on the speed of the final drive wheel 160 being 5 rpm. The 8-tooth drive wheel 160 is also connected to the 20-tooth drive wheel 164 at a ratio of 2.5:1, and the 20-tooth drive wheel 164 is connected to the 24-tooth drive wheel 166, resulting in a ratio of 1.2: 1.

Furthermore, the present invention includes a transmission that can withstand a significant amount of stress, strain, torque and friction because it uses a spline-type transmission wheel profile to distribute forces or loads over a greater surface area. The present invention includes a spline-shaped drive wheel configuration wherein the first drive wheel includes a first set of teeth extending over at least a portion of the drive wheel surface. The second drive wheel is engaged with the first drive wheel in a manner allowing the number of revolutions of the drive wheels relative to each other to be increased or decreased. In some cases, the drive wheels are curved or tapered to allow contact and allow for positioning and rotation of the drive wheels relative to each other. One example includes a conical gear that meshes with the second drive wheel. But the drive wheels may be circular, oval or other shapes if desired. Similarly, the second drive wheel may be conical, tapered, flat or even smooth, and the drive wheel shape may be any desired shape.

Furthermore, the teeth or grooves of the drive wheels of the present invention may have any size, shape, curvature, bevel, profile, etc. For example, the slots between the teeth may be curved, right angled, or any angle. Similarly, the tooth spacing and tooth height may be any desired dimension. For example, the top periphery of the teeth may be profiled, rounded, angled, smooth, etc. In addition, the present invention ensures meshing at different angles, and the ring gear and the pinion are merely an example. This combination allows the drive train or transmission to be configured at an angle between 0 and 90 degrees. The present invention provides in one embodiment a drive wheel speed reduction or increase and provides increased strength with a splined drive wheel drive mechanism of another embodiment.

FIG. 11A shows a top view of another embodiment of the transmission of the present invention. The drive wheel 200 includes a first drive wheel face 202 having two or more teeth 204 adapted to create friction between surfaces. The first drive wheel face 202 has two or more teeth 204 disposed about an outer portion of the first drive wheel face 202 and a central non-toothed face 206 in the first drive wheel face 202. The central relieved surface 206 also includes an opening 208, the size and shape of which may vary depending on the particular application. The first drive sheave face 202 includes a tooth face 210 and a tooth height 212. The tooth width 214 is the width of the tooth face 210 and is the distance from the first tooth height 212 to the second tooth height 212 and may vary depending on the particular application. The tooth surface 210 and tooth height 212 provide a frictional contact area when contacting another surface (not shown). The tooth width 214 and tooth height 212 may vary depending on the particular application and the particular amount of force applied to the drive wheel 200.

Fig. 11B and 11C show side views of the transmission mechanism shown in fig. 11A. The first drive wheel face 202 has two or more teeth 204 adapted to create friction between surfaces. The first drive wheel face 202 has two or more teeth 204 disposed about an outer portion of the first drive wheel face 202 and a central non-toothed surface (not shown) in the first drive wheel face 202. The first drive sheave face 202 includes a tooth face 210 and a tooth height 212. The tooth width 214 is the width of the tooth face 210 and is the distance from the first tooth height 212 to the second tooth height 212 and may vary depending on the particular application. The tooth surface 210 and tooth height 212 provide a frictional contact area when contacting another surface (not shown). The tooth width 214 and tooth height 212 may vary depending on the particular application and the particular amount of force applied to the drive wheel 200. In some embodiments, the tooth width 214 may be larger, while in other embodiments, the tooth width 214 may be smaller. Additionally, the first tooth height 212 is combined with the drive wheel base 218 thickness and is contained in the drive wheel thickness 216. The gear pitch line 220 and the tooth surface 210 form a gear pitch angle 222. The gear pitch angle 222 is generally the angle of the tooth surface 210. The angle may be different if the first tooth height 212 is not perpendicular to the gear pitch line 220. In some cases, the first tooth height 212 is not perpendicular to the gear pitch line 220, thereby creating an overhang from the first drive face 202 to the second drive face 202. Although the tooth surface 210 and tooth height 212 are shown as straight, other shapes may be used, including concave, convex, textured, and other surface treatments known to those skilled in the art.

FIG. 11D shows a perspective view of the drive system. The system includes a first drive wheel 200 and a second drive wheel 226, each having two or more drives on a first side and a second set of two or more teeth 254 extending from the periphery of the drive wheel at the drive wheel base 218. This embodiment can also be applied inside the drive wheel or inside the drive wheel and outside the drive wheel base 218, extending peripherally. Further, the pitch (distance between teeth) and the tooth angle or inclination (position relative to the base) may be modified and changed according to the purpose. In one embodiment, the first drive wheel 200 may be mounted around a drill bit such that the two or more teeth 204 on the drive wheel base 218 remove a ring of material as the drill bit drills through the material. In another embodiment, the first drive wheel 200 may be used as a lock washer. A bolt may be inserted into the first drive wheel 200, and the two or more teeth 204 function to lock the washer to the bolt or nut. In embodiments including two or more teeth 254, the teeth may be used to allow the nut and lock washer to be removed, if desired. A tool may contact the two or more teeth 254 to unscrew and remove the nut.

FIG. 11E shows a top view of another embodiment of the transmission of the present invention in combination with a ratchet insert (similar to a spline insert). The sleeve engagement portion 26 is designed to fit into a drive wheel cavity (not shown) in a similar manner to a conventional splined drive. The sleeve interface 26 includes a first drive wheel 200 and a second drive wheel 226, each having two or more teeth 204 on a first side and a second set of two or more teeth 254 extending out of the periphery of the drive wheel at the drive wheel base 218. A pawl (not shown) may engage the two or more teeth 204 on the first side and/or a second set of two or more teeth 254 to select the direction of rotation of the sleeve engagement portion 26. The sleeve engaging portion 26 includes a cylindrical recess 30 for receiving the spring 38 and the ball 32. The cylindrical recess 30, the spring 38, and the ball 32 are configured such that a portion of the ball 32 and the spring 38 are retained in the cylindrical recess 30, while the spring 38 biases another portion of the ball 32 out of the cylindrical recess 30. This allows the ball 32 to be pushed substantially into the cylindrical recess 30 while the sleeve (not shown) is being installed onto the sleeve engagement portion 26, but still presses against the sleeve (not shown) so that the sleeve (not shown) remains attached to the sleeve engagement portion 26. To remove the sleeve (not shown), the user simply pulls the sleeve (not shown) from the front face 28. The ball 32 is allowed to rotate whereby the user can more easily complete the movement of the sleeve. Of course, other arrangements may be used to retain a sleeve (not shown) to the sleeve engagement 26, and the illustrated embodiment should not be considered in any limiting sense.

FIG. 11F shows a top view of another embodiment of the transmission of the present invention in combination with a ratchet insert (similar to a spline insert). The sleeve engagement portion 26 is designed to fit into a drive wheel cavity (not shown) in a similar manner to a conventional splined drive. The sleeve engagement portion 26 includes a first drive wheel 200 and a second drive wheel 226, each having two or more teeth 204 on a first side and two or more sets of a second two or

more teeth

254a and 254b extending out of the periphery of the drive wheel at the drive wheel base 218. Two or more sets of a second set of two or

more teeth

254a and 254b may be in different directions to allow clockwise and counterclockwise rotation of the sleeve engagement portion 26. A pawl (not shown) may engage the two or more teeth 204 and/or two or more sets of a second set of two or

more teeth

254a and 254b on the first side to select the direction of rotation of the sleeve engagement portion 26. The sleeve engaging portion 26 includes a cylindrical recess 30 for receiving the spring 38 and the ball 32. The cylindrical recess 30, the spring 38 and the ball 32 are configured such that a portion of the ball 32 and the spring 38 are retained in the cylindrical recess 30, while the spring 38 biases another portion of the ball 32 out of the cylindrical recess 30. This allows the ball 32 to be pushed substantially into the cylindrical recess 30 while the sleeve (not shown) is being installed onto the sleeve engagement portion 26, but still presses against the sleeve (not shown) so that the sleeve (not shown) remains connected to the sleeve engagement portion 26. To remove the sleeve (not shown), the user simply pulls the sleeve (not shown) from the front face 28. The ball 32 is allowed to rotate whereby the user can more easily complete the movement of the sleeve. Of course, other arrangements may be used to retain a sleeve (not shown) to the sleeve engagement 26, and the illustrated embodiment should not be considered in any limiting sense.

Fig. 12A and 12B are schematic views of a double-sided drive wheel transmission system. The system includes a first drive wheel 200, an intermediate drive wheel 224 and a second drive wheel 226. The first drive wheel face 202 includes a drive wheel base 218 extending from the first drive wheel face 202 and includes two or more teeth 204 adapted to create friction between surfaces. The two or more teeth 204 extend from the outer edge of the pulley base 218 to a central relieved surface (not shown). The positioning cylinder 228 is located in the central relieved surface (not shown) and aligns the first drive wheel 200 with the intermediate drive wheel 224.

The intermediate drive wheel 224 includes a first intermediate drive wheel face 230 opposite a second intermediate drive wheel face 232. The positioning cylinder 228 is located in the central relieved surface (not shown) and aligns the first drive wheel 200 with the intermediate drive wheel 224. The positioning cylinder 228 may be a member of the first drive wheel 200, the intermediate drive wheel 224, either alone or in combination. The first intermediate drive sheave face 230 includes a first intermediate drive sheave base 234 extending from the first intermediate drive sheave face 230 and two or more first intermediate teeth 236 adapted to create friction between surfaces. The two or more first intermediate teeth 236 extend from the outer edge of the first intermediate drive wheel base 234 to a central relieved surface (not shown). The positioning cylinder 228 is located in the central relieved surface (not shown) and positions the two or more teeth 204 of the first drive wheel 200 and the two or more first intermediate teeth 236 of the intermediate drive wheel 224.

The second intermediate drive wheel face 232 includes a second intermediate drive wheel base 238 extending from the second intermediate drive wheel face 232 and two or more second intermediate teeth 240 adapted to create friction between the surfaces. The two or more second intermediate teeth 240 extend from the outer edge of the second intermediate drive wheel base 238 to a central relieved surface (not shown). A second positioning cylinder 242 is located in the central untouched surface (not shown) and aligns the two or more second intermediate teeth 240 with the second drive wheel 226.

The second drive wheel 226 includes a second drive wheel face 244 having a second drive wheel base 246 extending from the second drive wheel face 244 and two or more second teeth 248 adapted to create friction between the surfaces. The two or more second teeth 248 extend from the outer edge of the second drive wheel base 246 to a central relieved surface (not shown). A second positioning cylinder 242 is located in the central relieved surface (not shown) and positions the two or more second teeth 248 of the second drive wheel 226 and the two or more second intermediate teeth 240 of the intermediate drive wheel 224. The second drive wheel 226 includes a second rear face 250 and the first drive wheel 200 includes a first rear face 252. Additionally, the dual-sided drive wheel transmission system may be held together using a magnetic system having a plurality of magnets disposed between the first drive wheel 200 and the intermediate drive wheel 224 and between the intermediate drive wheel 224 and the second drive wheel 226.

In some embodiments, the first drive wheel 200 and/or the second drive wheel 226 may be molded into the housing of a larger device, such as a ratchet, wrench, crowbar, or the like. The intermediate transmission wheel 224 may be arranged to contact the first transmission wheel 200 or the second transmission wheel 226 by means of a magnetic selection mechanism or a mechanical selection mechanism, such as a pawl, a magnetic selection mechanism or a wedge-type selection mechanism. For example, a magnetic selection mechanism may be used to move the intermediate drive wheel 224 to contact the first drive wheel 200 and/or the second drive wheel 226. A wedge type selection mechanism may be used to move the intermediate drive wheel 224 to contact the first drive wheel 200 and/or the second drive wheel 226.

FIG. 12C shows a cross-sectional view of the double-sided drive wheel transmission system provided in the ratchet wrench 10 of the present invention. The ratchet wrench 10 includes a body (not shown) including a head portion 14 and a handle portion (not shown) extending from the head portion 14. A handle portion (not shown) is configured to be grasped by a user of the ratchet wrench 10. The head 14 contains a drive mechanism (as will be described in detail below) that is housed within a drive wheel cavity 48 formed between the body back side 20 and the front face 28.

The sleeve engaging portion 26 extends from a housing opening 70 in the body back side 20 for engaging a sleeve (not shown) or an elongate body (not shown). The socket engagement portion 26 includes a cylindrical recess (not shown) for receiving a spring (not shown) and a ball 32. The cylindrical recess (not shown), the spring (not shown), and the ball 32 are configured such that a portion of the ball 32 and the spring (not shown) are retained in the cylindrical recess (not shown) and the spring (not shown) biases another portion of the ball 32 out of the cylindrical recess (not shown). This allows the ball 32 to be pushed substantially into the cylindrical recess (not shown) while the socket (not shown) is being attached to the socket joint 26, but still to press against the socket joint 26. To remove the sleeve (not shown), the user need only pull on the sleeve (not shown). The ball 32 is allowed to rotate thereby allowing the user to more easily complete the sleeve movement. Of course, other arrangements may be employed to retain a sleeve (not shown) to the sleeve engagement portion 26.

The system includes a first drive wheel 200, an intermediate drive wheel 224 and a second drive wheel 226. The first drive wheel face 202 includes two or more teeth 204 adapted to create friction between surfaces. The two or more teeth 204 extend from the outer edge to a central non-toothed surface (not shown). The positioning cylinder 228 is located in the central relieved surface (not shown) and aligns the first drive wheel 200 with the intermediate drive wheel 224.

The intermediate drive wheel 224 includes a first intermediate drive wheel face 230 on the opposite side of a second intermediate drive wheel face 232. The positioning cylinder 228 is located in the central relieved surface (not shown) and aligns the first drive wheel 200 with the intermediate drive wheel 224. The positioning cylinder 28 may be a separate or combined component of the first drive wheel 200, the intermediate drive wheel 224. First intermediate drive sheave surface 230 includes two or more first intermediate teeth 236 adapted to create friction between surfaces. The two or more first intermediate teeth 236 extend from the outer edge of the first intermediate drive wheel base towards a central relieved surface (not shown). The positioning cylinder 228 is located within the central relieved surface (not shown) and aligns two or more teeth 204 of the first drive wheel 200 with two or more first intermediate teeth 236 of the intermediate drive wheel 224.

The second intermediate drive sheave surface 232 includes two or more second intermediate teeth 240 adapted to create friction between the surfaces. The two or more second intermediate teeth 240 extend from the outer edge of the second intermediate drive wheel base towards a central gearless face (not shown). The second positioning cylinder 242 is located in the central untouched surface (not shown) and the two or more second intermediate teeth 240 are aligned with the second drive wheel 226.

The second drive wheel 226 includes a second drive wheel face 244 having two or more second teeth 248 adapted to allow friction between surfaces. The two or more second teeth 248 extend from the outer edge of the second drive wheel base towards a central unmeshed surface (not shown). The second positioning cylinder 242 is located in the central relieved surface (not shown) and aligns two or more second teeth 248 of the second drive wheel 226 with two or more second intermediate teeth 240 of the intermediate drive wheel 224.

The first drive wheel 200, the intermediate drive wheel 224 and the second drive wheel 226 cooperate to control rotation of the socket engagement portion 26 relative to the ratchet wrench 10. As can be seen in fig. 12C, movement of the intermediate drive wheel 224 towards the first drive wheel 200 will cause the intermediate drive wheel 224 to engage the first drive wheel 200. The two or more teeth 204 engage the two or more first intermediate teeth 236 extending centrally of the periphery of the drive face. When rotated in one direction (a), the two or more teeth 204 pass over two or more first intermediate teeth 236 to allow unrestricted movement. Conversely, when the direction of rotation is in the opposite direction (B), the two or more teeth 204 contact the two or more first intermediate teeth 236 to limit rotation. The handle portion (not shown) of the ratchet wrench 10 is then free to rotate in the opposite direction (B), while rotation in the other direction (a) causes the component to lock and prevent rotation thereof, forcing the second drive wheel 226 to rotate the socket joint 26.

Conversely, movement of the intermediate drive wheel 224 toward the second drive wheel 226 will cause the intermediate drive wheel 224 to engage the second drive wheel 226. The two or more second intermediate teeth 240 engage two or more second teeth 248 extending from the gear face toward the center. When rotated in one direction (B), the two or more teeth 204 pass over two or more first intermediate teeth 236 to allow unrestricted movement. Conversely, when the direction of rotation is in the opposite direction (a), the two or more teeth 204 contact the two or more first intermediate teeth 236 to limit rotation. The handle portion (not shown) of the ratchet wrench 10 is then free to rotate in the opposite direction (a), while rotation in the other direction (a) causes the component to lock and prevent rotation to force the second drive wheel 226 to rotate the socket joint 26.

Fig. 13A is a schematic perspective view showing a transmission system. Fig. 13B to 13E are views of the transmission system. The system includes a first drive wheel 200 and a second drive wheel 226. The first drive wheel face 202 includes a drive wheel base 218 that extends from the first drive wheel face 202 and has two or more teeth 204 adapted to create friction between surfaces. The two or more teeth 204 extend from an outer edge of the pulley base 218 to a second set of two or more teeth 254. In some embodiments, the two or more teeth 204 and the second set of two or more teeth 254 are configured to face in opposite directions. The second set of two or more teeth 254 extend to a central relieved surface 256 disposed in

central openings

258 and 260. The second drive wheel 226 includes a second drive wheel face 244 having a second drive wheel base 246 extending from the second drive wheel face 226 and having two or more second teeth 248 adapted to allow friction between surfaces. The two or more second teeth 248 extend from an outer edge of the second drive wheel base 246 to a second set of two or more second teeth 262. The two or more second teeth 248 extend to a positioning cylinder 228 that extends outwardly from the plane of the second drive wheel base 246 so as to align with the central aperture 258 of the first drive wheel 200 and align the two or more teeth 204 of the first drive wheel 200 with the two or more first intermediate teeth 236 of the intermediate drive wheel 224. The positioning cylinder 228 is used to align two or more teeth 204 and two or more second teeth 248 and/or to align a second set of two or more teeth 254 and a second set of two or more second teeth 262.

The first and

second drive wheels

200, 226 each include a drive wheel face (not shown) having a tooth face (not shown) and a tooth height (not shown). The tooth width (not shown) is the width of the tooth surface (not shown) and is the distance from the first tooth height (not shown) to the second tooth height (not shown), and may vary depending on the particular application. The tooth flanks (not shown) and tooth heights (not shown) provide a frictional contact area when contacting opposing tooth flanks (not shown) and tooth heights (not shown). The tooth width (not shown) and tooth height (not shown) may vary depending on the particular application and the particular amount of force applied to the drive wheel (not shown). Further, the superposition of the first tooth height (not shown) and the thickness of the drive wheel base is contained in the drive wheel thickness (not shown). The gear pitch angle (not shown) is typically the angle of the tooth face (not shown). The angle may be different if the first tooth height (not shown) is not perpendicular to the tooth pitch line (not shown) to create an overhang from the first drive wheel face (not shown) to the second drive wheel face (not shown).

Fig. 14A, 14B and 14C are views of the drive system of fig. 13, with the drive wheels separated in fig. 14A, aligned in fig. 14B and engaged in fig. 14C.

FIGS. 15A and 15B are diagrams of the transmission system of FIG. 14 adapted for incorporation into a coupling assembly of a larger device. Fig. 15A is a view of the first drive wheel 200 in the head 264 on the first side 266 of the device in alignment with the second drive wheel 226 in the head 268 on the other half 270 of the device. The first drive wheel 200 includes two or more teeth 204 and a central opening 258 that is aligned with the positioning cylinder 228 for aligning the two or more teeth 204 with the two or more second teeth 248.

Fig. 15B is a cross-sectional view of the first drive wheel 200 in the head 264 of the first side 266 of the device in alignment with the second drive wheel 226 in the head 268 of the other half 270 of the device. The first drive wheel 200 includes two or more teeth 204 and a central opening (not shown) that receives a positioning cylinder (not shown) for aligning the two or more teeth 204 with the two or more second teeth 248.

FIG. 16 is a view of the drive system of the present invention disposed in a crowbar. The crowbar 272 includes a first bar 274 and a second bar 276 connected by a drive wheel coupling assembly 278. The drive wheel coupling assembly 278 includes a first drive wheel (not shown) located within the head 264 of the first rod 274 and a second drive wheel (not shown) located within the head 268 of the second rod 276. The first drive wheel (not shown) includes two or more teeth (not shown) that align with two or more second teeth (not shown) for securing the crowbar in place and allowing the drive wheel coupling assembly 278 to fail under extreme stress.

Furthermore, the present invention provides one set of actuators (e.g., gears, textures, grooves, etc.) that mesh with another set of actuators, wherein the actuators are distributed over a substantial portion of the surface to provide an extended contact area, thereby providing greater strength. The set of drive mechanisms may be configured to form a two-piece drive wheel coupling which may itself be part of a larger device, wherein the two-piece drive wheel coupling may be separated or rotated to act as a folding coupling, wherein when rotated and reset, the drive wheel sets realign and form a strong coupling. This embodiment may be used in any device requiring a configuration that is both strong and flexible, such as crowbars, hammers, legs, ladders, brackets, and the like.

In some embodiments, a magnet may be used to engage and disengage the two-piece pulley connection joint such that the magnetic engagement structure may be engaged to disengage the two-piece pulley connection joint, the two-piece pulley connection joint may be moved into position, and the magnetic engagement structure may be disengaged to provide a stable, non-moving structure. Similarly, the two-piece drive wheel connection joint may include multiple joints, to allow for the inclusion of a variety of different configurations, including a variety of derivative configurations or combinations thereof, resulting from a set of overlapping joints or multiple joints along a single member.

In another embodiment, the ratchet mechanism includes a ratchet wheel formed by a first drive wheel, a second drive wheel, a ratchet housing, and an intermediate drive wheel having a first intermediate drive wheel face located on an opposite side of the second intermediate drive wheel coupled to the handle.

The ratchet wheel includes a first drive wheel end surface and a second drive wheel end surface separated by a lever. The first drive wheel end surface includes a drive wheel base having two or more teeth on a first face on an opposite side of the first drive wheel from the back face. The second drive wheel end surface also includes a second drive wheel base having two or more second teeth on a second face opposite the second drive wheel back face. The first and second drive wheel end surfaces separated by the bar are positioned such that two or more teeth on the first face are directed towards two or more teeth on the second face.

The intermediate drive wheel includes a first intermediate gear face located on an opposite side of a second intermediate drive wheel face connected to the handle. The ratchet housing is adapted to assemble the ratchet wheel and the intermediate drive wheel such that the first intermediate drive wheel face is opposite the first drive wheel end surface and the second drive wheel end surface is opposite the second intermediate drive wheel face.

The ratchet housing is adapted to assemble the ratchet wheel and the intermediate drive wheel such that the first intermediate drive wheel face is opposite the first drive wheel end surface and the second drive wheel end surface is opposite the second intermediate drive wheel face. The intermediate drive wheel includes a first intermediate drive wheel face engaging two or more teeth on the first drive wheel face. The opposing second intermediate gear face does not contact two or more teeth on the second gear face that are moved into the ratchet housing. Similarly, the reverse operation can be performed, by moving the intermediate drive wheel in such a way that the first drive wheel face is moved into the ratchet housing. This arrangement ensures that the second intermediate drive sheave surface contacts the two or more teeth on the second drive sheave surface. The first intermediate gear face does not contact the first intermediate gear face to engage two or more teeth that are moved into the ratchet housing.

The ratchet housing includes an engagement tip and is adapted to mount the ratchet and the intermediate drive wheel such that a first intermediate drive wheel face is located opposite the first drive wheel end surface and an opposing second intermediate drive wheel face engages the engagement tip. The first intermediate drive wheel face does not engage a first drive wheel end surface located within the ratchet housing.

Fig. 17A is an exploded view of another embodiment of the present invention, specifically a wrench 410. Wrench 410 includes a body 412 having a head portion 414a and a handle portion 416 connected to a second head portion 414 b. Handle portion 416 is configured to be grasped by a user of wrench 410 and may include textured and/or non-textured regions 418. The

heads

414a and 414b include

bolt holes

420a, 420b for receiving bolts, nuts, or other fasteners. One or both of the heads 414 may be connected to the main body 412 by a hinge 422 having a hinge body housing 424 and a hinge body opening 426 that mate with a hinge head housing 428 and a hinge head opening 430. Alignment of the hinge 422 allows installation with the hinge pin 432, providing for swinging and movement about the hinge 422. The head 414a includes a drive wheel cavity 434 for receiving a drive mechanism 436 located between a body back side 438 and a front face 440 of the ratchet wrench 410. Front face 440 includes bolt holes 420a and bolt hole slots 442 extending through front face 440 to allow access to bolt holes 420 a. The transmission mechanism includes first and

second drive wheels

446 and 448 having

bolt hole slots

442 and 450, respectively, extending through the front face 440 to allow access to the bolt holes 420 a. When aligned, the tool may pass a bolt from outside the bolt hole 420a into inside the bolt hole 420 a.

The pulley cavity 434 includes a first pulley 446 having a first pulley surface 452 including two or more first pulley teeth 454 extending centrally across the first pulley surface 452 from a periphery thereof adapted to allow friction between surfaces. The second drive wheel 448 includes a second drive wheel face 456 having two or more second drive wheel teeth 458 extending centrally across the second drive wheel face 456 from a periphery thereof to engage the two or more first drive wheel teeth 454 of the first drive wheel face 452 to allow friction between the surfaces. When rotated in one direction, the two or more first drive gear teeth 454 pass over the two or more second drive gear teeth 458 to allow unrestricted rotation. Conversely, when the direction of rotation is in the opposite direction, the two or more first gear teeth 454 contact the two or more second gear teeth 458 to restrict rotation. Two or more first drive gear teeth 454 and two or more second drive gear teeth 458 extend from the peripheral edge across the drive wheel face toward the center, which allows for a larger contact area between each tooth pair, thereby increasing strength. A stop collar 460 and shim 462 are used to position the drive mechanism 436 between the body back side 438 and the front face 440 of the ratchet wrench 410.

Fig. 17B is an exploded view of a head 414a including a bolt hole 420a for receiving a bolt, nut, or other fastener. The head 414a includes a hinge head housing 428 and a hinge head bore 430. The head 414a includes a drive wheel cavity 434 for receiving a drive mechanism 436 located between a body back side 438 and a front face 440 of the ratchet wrench 410. Front face 440 includes bolt holes 420a and bolt hole slots 442 through front face 440 to allow access to bolt holes 420 a. The transmission mechanism includes a first transmission wheel 446 and a second transmission wheel 448, each having a

bolt hole slot

442 and 450, respectively, extending through the front face 440 to allow access to the bolt hole 420 a. When aligned, the tool may pass a bolt from outside the bolt hole 420a into inside the bolt hole 420 a.

The pulley cavity 434 houses a first pulley 446 having a first pulley surface 452 including two or more first pulley teeth 454 extending centrally across the first pulley surface 452 from a periphery thereof adapted to allow friction between the surfaces. The second drive wheel 448 includes a second drive wheel face 456 having two or more second drive wheel teeth 458 extending centrally from a periphery of the second drive wheel face 456 across the second drive wheel face to engage the two or more first drive wheel teeth 454 of the first drive wheel face 452 to allow friction between the surfaces. When rotated in one direction, the two or more first drive gear teeth 454 pass over the two or more second drive gear teeth 458 to allow unrestricted rotation. Conversely, when the direction of rotation is in the opposite direction, the two or more first gear teeth 454 contact the two or more second gear teeth 458 to restrict rotation. Handle 416 of ratchet wrench 410 is then free to rotate in this opposite direction, and rotation in the other direction causes the components to lock and prevent rotation, forcing second drive wheel 448 to rotate.

Two or more first drive gear teeth 454 and two or more second drive gear teeth 458 extend from the peripheral edge across the drive wheel face toward the center, which allows for a larger contact area between each tooth pair, thereby increasing strength. A stop collar 460 and shim 462 are used to position the drive mechanism 436 between the body back side 438 and the front face 440 of the ratchet wrench 410.

Although the figures show a solid wrench, it will be apparent to those skilled in the art that the present invention may be used with both closed and notched wrenches. Body 412 may include

head portions

414a and 414b coupled to handle portion 416, which may be rotated 0-90 degrees relative to head portions 414a and/or 414 b. Further, handle portion 416 may be curved, angled, slanted, raised, lowered, or tapered with respect to one or both

head portions

414a and 414 b.

Another embodiment of the present invention includes a bolt hole 420a having a splined inner surface. The head 414a includes a bolt hole 420a for receiving a bolt, nut, or other fastener. The head 414a includes a hinge head housing 428 and a hinge head bore 430. The head 414a includes a drive wheel cavity 434 for receiving a drive mechanism 436 located between a body back side 438 and a front face 440 of the ratchet wrench 410. Front face 440 includes bolt holes 420a and bolt hole slots 442 extending through the front face to allow access to bolt holes 420 a. The transmission mechanism includes a first transmission wheel 446 and a second transmission wheel 448, each having a

bolt hole slot

442 and 450, respectively, extending through the front face 440 to allow access to the bolt hole 420 a. When aligned, the tool may pass a bolt from outside the bolt hole 420a into inside the bolt hole 420 a. Bolt hole 420a may include a splined inner surface having splines distributed around bolt hole 420 a. The splines distributed around the bolt holes 420a allow the spline gear or sleeve to be inserted into the bolt holes 420a such that the splined inner surface contacts the splines of the spline gear or sleeve. Additionally, the splined inner surface surrounding bolt hole 420a allows the hole to accommodate a variety of different nuts and bolts, such as square, hex, 0-65% round hex, quincunx, 0-65% round hex, slotted, Torx star, and the like.

Fig. 18A and 18B are exploded isometric views of the transmission of fig. 17, as would be suitable for use in a coupling assembly for a large device. The coupling assembly may be used in a number of devices including crowbars, rods, posts, clamps, ladders, scaffolding, easels, legs, tables, and the like.

Fig. 18A is an exploded isometric left side view including a coupling assembly 470 including a first body 472 mated with a second body 474. The first body 472 includes a first connection end 476 proximate to a first head 478. First head 478 includes a drive wheel cavity 480 within first head 478 for receiving a spring, spacer or washer 482 (if any) and a first drive wheel 484 positioned between body back side 486 and front face 488. The first drive wheel 484 includes a first drive wheel back surface 490 on an opposite side of the first drive wheel face 492 that includes two or more first drive wheel teeth 494 that extend centrally across the first drive wheel face 492 from a periphery thereof and are adapted to allow friction between the surfaces. A first alignment hole 496 is provided in the center of the first drive wheel 484 to assist in the alignment of the first drive wheel 484. The second body 474 includes a second connection end 498 proximate the second head 500. The second header 500 includes a separation groove 502 extending into at least a portion of the second header 500 from the outside. Within the separator tank 502 are a plurality of separator holes 504 that extend from the separator tank 502 through the second header 500. A separator spring/washer 506 is located within separator groove 502. A release mechanism 508 is disposed in contact with the spring/washer 506 and a plurality of release pins 510 pass through the plurality of release holes 504 and are secured by a retaining clip 512.

Fig. 18B is an exploded isometric right side view including a coupling assembly 470 including a first body 472 mated with a second body 474. The first body 472 includes a first connection end 476 proximate to a first head 478. First head 478 includes a drive wheel cavity (not shown) within first head 478 for receiving a spring, pad or washer (as may be) and a first drive wheel 484 positioned between body back side 486 and front face (not shown). First drive wheel 484 includes a first drive wheel back surface 490 on an opposite side of a first drive wheel face (not shown) that includes two or more first drive wheel teeth 494 that extend from a periphery of the first drive wheel face (not shown) across the drive wheel face toward the center and are adapted to allow friction between the surfaces. A first alignment hole 496 is provided in the center of the first drive wheel 484 to assist in the alignment of the first drive wheel 484.

The second body 474 includes a second connection end 498 proximate the second head 500. The second head 500 includes a second drive wheel 516 having a second drive wheel face 518 including two or more second drive wheel teeth 520 extending centrally across the drive wheel face from the periphery of the second drive wheel face 518 to engage with two or more first drive wheel teeth 494 of a first drive wheel face (not shown) to allow friction between the surfaces. An alignment rod 522 extends from the second body 474 and extends through the second head 500 and the second drive wheel face 518 to align the link assembly 470. A plurality of disengagement apertures 504 are provided around the alignment rod 522 to provide a mechanism for allowing the first drive wheel 484 to move away from the second drive wheel 516. A separator spring/washer (not shown) is located within a separator groove (not shown). The disengagement mechanism 508 is disposed in contact with a spring/washer (not shown) to apply a bias, and a plurality of disengagement pins 510 are passed through the plurality of disengagement apertures 504 and secured by a retention clip 512.

In operation, the crowbar extends from the first connection end 476 adjacent the first head 478 and the second connection end 498 adjacent the second head 500. Located between the first head 478 and the second head 500 is a drive wheel pocket 480 which houses a spring 482 biased away from the first head 478. The first drive wheel 484 is aligned by the alignment rod 522 and bears against the spring 482. First drive wheel 484 is also abutted against second drive wheel 516 such that two or more first drive gear teeth 494 are engaged with two or more second drive gear teeth 520, thereby restricting free movement of first drive wheel 484 or second drive wheel 516. The second head 500 includes a disengagement slot 502 in which is housed a disengagement mechanism 508 that contacts a spring/washer 506 and includes a plurality of disengagement pins 510 that pass through a plurality of disengagement apertures 504 and are secured by a retention clip 512.

When the release mechanism 508 is pressed, the spring/washer 506 is depressed and the release pin 510 moves inwardly through the plurality of release apertures 504 and against the first drive wheel 484, thereby compressing the spring, washer or washer 482 and releasing the first drive wheel 484 from the second drive wheel 516.

FIG. 19 is an exploded isometric view of the transmission of FIG. 18, adapted to assemble a multiplier gear set. The linkage assembly may be used in a variety of devices, including crowbars, door entry devices, swing jaws, jacks, cranes, and the like. Coupling assembly 524 includes a first body 526 and a second body 528 that mate with two sides of a hinge base 530. The first body 526 includes a first connection end 532 proximate a first head 534. First head 534 includes a gear cavity 536 within first head 534 for receiving a first gear shaft 538 coupled to a first gear portion 540, here a planetary gear, but could be another type of drive wheel. Hinge mount 530 includes a first hinge mount side 542 and a second hinge mount side 544 separated by an annular gear aperture 546. First hinge mount side 542 is adapted to mate with first head 534. The ring gear aperture 546 receives a ring gear 548. In this embodiment, the ring gear aperture 546 is polygonal, but may have any other desired shape. The hinge base 530 includes a bottom 550 having a flat bottom surface for supporting the hinge base assembly. Further, the ring gear aperture 546 and the ring gear 548 may be constructed of a single piece and integrated into a single device. The size, shape, material, location, etc. may vary depending on the particular application. The ring gear 548 includes an internal bore 552 with a plurality of internal ring teeth 554 thereon. The outer wall 556 is configured to be secured within the ring gear aperture 546. A set of gears 558 is positioned in the bore 552 to contact the inner ring of teeth 554 and the first gear portion 540. The set of gears 558 can include 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or more gears having different or similar pitches. The set of gears 558 is coupled to a second body 528 that includes a second coupling end 560 proximate a second head 562. In operation, application of force to the first link end 532 causes the first gear portion 540 to move, and as the first gear portion moves, the set of gears 558 interacting therewith causes the second body 528, including the second link end 560, to move. The amount of force required may vary with the particular gears and gear ratios used in the present invention.

Fig. 20A is an exploded isometric view of a gear assembly with multiple jaws and a single swing handle and a multiplier gear set. The opening mechanism 570 may also be used in a variety of devices including crowbars, door entry devices, swing jaws, jacks, cranes, and the like. The opening mechanism 570 includes a first body 572 and a second body 574 that mate to the two sides. The first body 572 includes a gear cavity 576 within the first body 572 for receiving a set of gears 578, which in this embodiment includes a transfer gear 580 and a pair of

jaw gears

582a and 582 b. The drive gear 580 functions to drive the pair of

jaw gears

582a, 582b, which may be accomplished at similar gear ratios using

similar jaw gears

582a and 582b, or at different gear ratios using gears having different gear ratios. The set of gears 558 may include 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or more gears having different or similar pitches. Jaw gears 582a and 582b (which may also be of unitary construction)

house shafts

584a and 584 b.

Jaws

586a and 586b are coupled to

shafts

584a and 584b such that rotation of drive gear 580 drives rotation of

jaw gears

582a and 582b, which in turn drives

jaws

586a and 586 b. The amount of force required may vary depending on the particular gears and gear ratios used in the present invention. The drive gear 580, jaw gears 582a and 582b,

shafts

584a and 584b, and

jaws

586a and 586b are movably mounted between the first body 572 and the second body 574. The drive gear 580 includes an insert hole 588 configured to receive the ratchet insert 590. The ratchet insert 590 is fixed in the insert hole 588 of the transmission gear 580. The ratchet handle 592 has a first connection end 594 adjacent the first head 596. First head 596 has a securement aperture 598 for securing ratchet handle 592 to second body 574. The separator mechanism 600 is disposed in contact with a spring/washer (not shown) to achieve biasing, and a plurality of separator pins 602 pass through a plurality of separator holes 604 and are secured by a retaining clip (not shown). A first gear rod 606 extends from the first head 596 for alignment and abutment against the spring 482. First head 596 includes a second gear (not shown) that cooperates with ratchet insert 590 to limit free movement.

Fig. 20B is an isometric perspective view of the transmission with multiple jaws and a single swing handle and multiplier gear set. The opening mechanism 570 may also be used in a variety of devices including crowbars, door entry devices, physical jaws, jacks, cranes, and the like. The opening mechanism 570 includes a first body 572 and a second body 574 that mate to the two sides. The first body 572 includes a gear cavity (not shown) within the first body 572 for receiving a set of gears (not shown) and a pair of jaw gears (not shown). Rotation of ratchet handle 592

drives jaws

586a and 586 b. The amount of force required varies depending on the particular gears and gear ratios used in the present invention. Ratchet handle 592 includes a first connection end 594 adjacent first head 596. First head 596 has a disengagement mechanism 600 for moving ratcheting handle 592 without moving

jaws

586a and 586 b.

FIG. 21 is an exploded isometric view of a gear drive mechanism having a multiplier gear set used as a drive extension structure. The drive extension structure may be used in a variety of devices, including ratchets, sleeves, transmissions, drivelines, and the like. The drive extension 610 includes mating first and

second bodies

612, 614. The first body 612 includes a first connection end 616 proximate the first gear portion 618. First head 612 includes a gear cavity 620 within first head 612 for receiving a first coupling end 616, here a planetary gear, but which could be another type of drive wheel, connected to a first gear portion 618 by a rod 622. The first body 612 includes a ring gear aperture 624 for receiving a ring gear 626, in this embodiment the ring gear aperture 624 is polygonal, but may have other desired shapes. The ring gear aperture 624 and the ring gear 626 may be constructed of a single piece and integrated into a single device. The size, shape, material, location, etc. may vary depending on the particular application. The ring gear 626 includes an internal bore 628 with internal ring teeth 630 thereon. The outer wall 632 is configured to be secured within the ring gear aperture 624. A set of gears 634 is positioned in the internal bore 628 in contact with the inner ring teeth 630 and the first gear portion 618. The set of gears 634 may include 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or more gears having different or similar tooth pitches. The set of gears 634 is coupled to the second body 614 having a second coupling end 636 proximate the second body 614. Second coupling end 636 also includes a second coupling aperture 638 that is configured to receive a drive mechanism (not shown), which may be a socket, ratchet, wrench, head, extension, bit, drill bit, and other instruments known in the art. A thumb wheel 640 is also attached to the second body 614 and may be secured by a screw 642 and a weld (not shown). The rod 622 is connected to one or more washers 644, a biasing mechanism 646, a first sliding end piece 648 and a second sliding end piece 650. In operation, the second coupling hole 638 is loaded into the ratchet. When the ratchet rotates, the lever 622 rotates and causes the set of gears 634 to rotate and the first gear portion 618 rotates the first connection end 616. The first connection end 616 may be adapted to receive ratchets, wrenches, heads, extensions, bits, drills, and other instruments known in the art. In another embodiment, the ring gear 626 includes an inner bore 628 with inner ring teeth 630 thereon, and an outer wall 632 is configured to be secured within the ring gear bore 624. The set of gears 634 are positioned so as to allow an interchangeable connecting gear (not shown) to be inserted and removed, the connecting gear having a first connecting end 616 connected to a first gear portion 618 by a rod 622. A shiftable connection gear (not shown) may be inserted in a similar manner as a spline driven wrench and allow for shifting different drive sizes (1/4, 1/2, 3/4, 1, etc.) at the first connection end 616.

FIG. 22 is an exploded isometric view of a gear assembly including a compound multiplier gear set as a drive extension. The drive extension structure may be used in a variety of devices, including ratchets, sleeves, transmissions, drivelines, and the like. The drive extension 610 includes a first body 612 and a second body 614 that include a first gear set 644 and a second gear set 646 for providing different multi-step gear ratios. The rod 622 extends through the first plate aperture 648 into the first connection end 616 on one side of the first gear plate 650, with the first gear portion 618 disposed on the opposite side of the first gear plate 650. The first connection end 616 may be adapted to receive ratchets, wrenches, heads, extensions, bits, drills, and other instruments known in the art. The first set of gears 634 is disposed about the first gear portion 618 and sandwiched between the first gear plate 650 and the second gear plate 652. The second gear portion 654 is disposed on an opposite side of the second gear plate 652. In this example a planetary gear, but other types of transmission wheels are possible. First head 612 includes a first gear cavity (not shown) and a second gear cavity 656 within first head 612 to receive second gear portion 654 through an opening (not shown). The second set of gears 658 is positioned in the second gear cavity 656 and contacts the second gear portion 654. A second set of gears 658 is mounted between the first body 612 and the second body 614. The second body 614 includes a second coupling end 636 and a second coupling aperture 638 that are configured to receive a drive mechanism (not shown) that may be a socket, ratchet, wrench, head, extension, bit, drill bit, and other instruments known in the art. The gear sets may include 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or more gears having different or similar tooth pitches. The drive extension 610 may be secured at one end by a ring 660 and at the other end by a ring 662.

In operation, the second coupling hole 638 is attached to a device. When the second link 636 is rotated, the second set of gears 658 are rotated and cause the second gear portion 654 to rotate. As the second gear portion 654 rotates, the second gear plate 652 and the first set of gears 634 rotate, thereby moving the first gear portion 618 and the rod 622, which extends through the first plate aperture 648 into the first connection end 616. The first connection end 616 may be connected to other devices such as a socket, ratchet, wrench, head, extension, bit, drill bit, and other instruments known in the art. The first and second gear sets 644, 646 control the gear ratios input to the output transmission, such as 10:1, 12:1, 15:1, 25:1, 50:1, etc.

Fig. 23A to 23D are isometric views of the hinge wrench. Fig. 23A is a view of an articulated wrench having a half thickness, and fig. 23D is a view of an articulated wrench having a full thickness. The following embodiments may be full thickness or half thickness, but are shown here in half thickness for illustration. Fig. 23B is a view of a bending hinge wrench and fig. 23C is a view of a twisting hinge wrench. Fig. 23A is a view of an articulated wrench. Hinge wrench 700 includes a handle 702 coupled to lower hinges 704a-704e and an upper hinge 706.

Fig. 24A-24C are isometric views of components of the hinge wrench. Fig. 24A is an isometric view of a handle 702 that includes a handle portion 708 and a handle connection end 710. Handle attachment end 710 includes a release button aperture 712 that receives a release button 714 having a spring/washer 716 and a retaining ring 718. A breakaway spring/washer 716 is positioned in breakaway button aperture 712 below breakaway button 714 to apply a bias. The disengage button aperture 712 includes one or more disengage apertures 720 that receive one or more disengage pins 722 on the disengage button 714. Opposite the release button 714 is an alignment post 724 for assisting in alignment of the components.

Fig. 24B is an isometric view of the lower hinge 704, which includes a lower hinge receiving end 726 and a lower hinge connecting end 728. The lower hinge connection end 728 includes the release button aperture 712 that receives the release button 714 with the spring/washer 716 and the retaining ring 718. A breakaway spring/washer 716 is positioned in breakaway button aperture 712 for biasing under breakaway button 714. The disengage button aperture 712 includes one or more disengage apertures 720 that receive one or more disengage pins 722 on the disengage button 714. Opposite the release button 714 is an alignment post 724 for assisting in alignment of the components. The lower hinge receiving end 726 includes a receiving cavity (not shown) for receiving the spring/washer 730 and the slug 732.

Fig. 24C is an isometric view of upper hinge 706, which includes upper hinge receiving end 734 and upper hinge connecting end 736. The upper hinge receiving end 734 includes a first nest aperture 738 for receiving the spring/washer 730 and the slug 732. The sides of the first nest hole 738 are designed to receive and secure the spring/washer 730 and the slug 732. The slug 732 includes a slug hole 740 and an alignment rod hole 742. Upper hinge end 728 includes a fitting 744 for receiving a wrench, socket, ratchet, nut, bolt, etc., and may include a retaining ball 746 and a retaining spring 748 that is inserted into a ball hole 750.

Fig. 24D is an isometric view of the lower hinge 704, which includes a lower hinge receiving end 726 and a lower hinge connecting end 728. The lower hinge link end 728 includes a release button aperture (not shown) on the opposite side that receives a release button (not shown) on the opposite side. The release button apertures (not shown) include one or more release apertures 720 that receive one or more release pins (not shown) of the release button (not shown). An alignment rod 724 is provided opposite the release button (not shown) to aid in alignment of the components. The second inlay hole 752 is disposed around the alignment rod 723 and includes the one or more separation holes 720 that receive the one or more separation pins.

Fig. 24E is an isometric view of the hinge wrench assembly. Hinge wrench 700 includes a handle 702 connected to lower

hinges

704a, 704b and upper hinge 706. The handle 702 includes a breakaway button 714 on the opposite side of an alignment bar 724 that is used to aid in alignment and securing of the components. The handle 702 is mated with the lower hinge 704a such that the slug 732 and spring are positioned between the first nest hole 738 and a second nest hole (not shown) around the alignment rod 724. The release button 714 contacts the alignment rod 724, and thus pressing the release button 714 disengages the insert 732 from the second insert hole (not shown) so that the handle 702 can rotate relative to the lower hinge 704. The release of the disengage button 714 causes the slug 732 to be repositioned within the first nest hole 738 and the second nest hole (not shown) around the alignment rod 724. The release button 714 can also be depressed to allow the lower hinge 704 to be separated from the handle 702 for disassembly of the wrench. The lower hinge 704a is connected to the lower hinge 704 b. The lower hinge 704a includes a release button (not shown) on the opposite side of the alignment rod 724 that is used to assist in alignment and securing of the components. The lower hinge 704a is engaged with the lower hinge 704b such that the insert 732 and the spring 730 are positioned between the first insertion hole (not shown) and the second insertion hole 752. The release button 714 contacts the alignment rod 724, and thus pressing the release button 714 disengages the slug 732 from the second insertion hole 752, such that the lower hinge 704a may rotate relative to the lower hinge 704 b. Release of the release button (not shown) causes the slug 732 to be repositioned in the first slug hole (not shown) and the second slug hole 752 around the alignment rod 724. The disengage button 714 can also be pressed to allow the lower hinge 704a to disengage from the lower hinge 704b to disassemble the wrench. The lower hinge 704b is connected to the upper hinge 706. The lower hinge 704b includes a breakaway button 714 on the opposite side of an alignment bar 724 that is used to aid in alignment and securing of the components. The lower hinge 704b mates with the upper hinge 706 such that the slug 732 and spring 730 are positioned between the first nest hole 738 and a second nest hole (not shown) near the alignment rod 724. The disengage button 714 contacts the alignment rod 724, and thus depressing the disengage button 714 disengages the slug 732 from the second insert hole (not shown) so that the lower hinge 704b can rotate relative to the upper hinge 706. The release of the disengage button 714 causes the slug 732 to be repositioned within the first nest hole 738 and the second nest hole (not shown) around the alignment rod 724. The disengage button 714 can also be depressed to allow the lower hinge 704b to disengage from the upper hinge 706, thereby disassembling the wrench. The upper hinge 706 includes a fitting 744 for receiving a wrench, socket, ratchet, nut, bolt, etc., and may include a stop ball 746.

In another embodiment, the hinge wrench may have a conventional wrench shape with a first end and a second end separated by a rod. The two ends may be independently selected from box ends, openings, ratchet wrenches, brake wrenches, and the like. The lever may have one or more hinges to allow the wrench to bend and swivel as desired. For example, the rod may have an upper hinge and a lower hinge connected by a hinge joint. The upper hinge includes a release button on the opposite side of the alignment rod that is used to assist in the alignment and securing of the components. The upper hinge is mated with the lower hinge such that the slug and the spring are positioned between the first inlay hole and the second inlay hole around the alignment rod. The release button contacts the alignment rod, and thus depressing the button moves the slug out of the second nest aperture so that the upper hinge is rotatable relative to the lower hinge. Release of the release button causes the slug to be repositioned in the first nest hole and the second nest hole around the alignment rod. Another embodiment allows the release button to be depressed to allow the lower hinge to be separated from the upper hinge for disassembly of the wrench. In some embodiments, there are 1, 2, 3, 4 or more hinges in a single wrench.

Fig. 25A-25C are views of a telescoping pole used with a crowbar, support pole, or other implement described herein. Fig. 25A shows the first lever 760 being slidable into the second accommodating lever 762. The length of the telescopic rods can be adjusted according to specific needs and can be manufactured in different lengths. The first rod 760 includes one or more openings 764 that secure a locking pin (not shown) located in the second receiving rod 762. When the release button 766 is pressed, a locking pin (not shown) may be disengaged and the length may be adjusted. Fig. 25B shows a first rod 760 that can be slid into the second receiving rod 762 and has the coupling assembly 278 on the first rod 760. Some device (e.g., an anti-slip tripod, wedge, hammer, fork, axe, etc.) may be mounted on the first lever 760, the second accommodating lever 762, or both. Fig. 25C shows a first lever 760 which is square and can be slid into a second accommodating lever 762 which is round, but the inventor in the art can adopt such a structure or make modifications.

Fig. 26A, 26B and 26C show end face drive wheel assembly views with reversing mechanisms. Any embodiment given or contemplated by the present invention may include a compound drive wheel set having one face drive wheel set in the second face drive wheel and a plurality of teeth in opposite directions. For example, fig. 26A is an exploded isometric view of the transmission showing a dual face drive wheel set with a selector switch for selectively engaging the face drive wheels in a particular direction. In fig. 26A, a first body (not shown) mates with a second body 474. The second body 474 includes a second connection end 498 proximate the second head 500. The second header 500 includes a separation groove 502 extending inward from the outside into at least a portion of the second header 500. One or

more detachment holes

504a and 504b are provided in the detachment slot 502 and extend from the detachment slot 502 through the second header 500. The second header 500 includes a second header end face drive wheel aperture (not shown) adapted to receive a first end face drive wheel 484a located within the second header end face drive wheel aperture (not shown) and a second first end face drive wheel 484b located within the first end face drive wheel 484 a. The first end face drive wheel 484a includes two or more first drive gear teeth 494a that extend centrally across the wheel face from the periphery of the first drive wheel face (not shown) and are adapted to allow friction to be generated between the surfaces. The second first end face drive wheel 484b includes two or more first drive gear teeth 494b that extend centrally across the wheel face from the periphery of the first drive wheel face (not shown) and are adapted to allow friction to be generated between the surfaces. The first end drive wheel 484a may include a first alignment aperture 496a for facilitating alignment of the first end drive wheel 484 a. The second first end drive wheel 484b fits into the first alignment aperture 496a, the shape of the first alignment aperture 496a may be any desired shape and may secure the first end drive wheel 484a to the second first end drive wheel 484 b. However, the first alignment hole 496a may be circular, and the second first end drive wheel 484b is secured by the decoupling pins 510a, 510b, 510c, and 510d extending through the one or

more decoupling holes

504a and 504 b. The second first end drive wheel 484b also includes a first alignment aperture 496b that is adapted to receive the positioning cylinder 228. The positioning cylinder 228 positions the second first end drive wheel 484b in the first end drive wheel 484a and the second head 500. The first end drive wheel 484a and the second first end drive wheel 484b have biasing

mechanisms

482a, 482b, 482c, 482d for biasing the first end drive wheel 484a and the second first end drive wheel 484b away from the one or

more disengaging apertures

504a and 504 b. In some embodiments, the device may include a reversing mechanism that includes a knob 24 disposed at least partially over the one or

more separation apertures

504a and 504 b. The swing handle 24 has a set of two jaws (

inner jaw

25a, 25b and

outer jaw

25c, 25d), each pair being located at the end of the swing handle 24 and connected by two

sections

23a and 23 b. The reverse member 22 has a top portion extending through the body back side 20 and is thus movable fore and aft. The inversion member 22 has 2 sets of attachment ends 27a and 27b that mate with the 2

sections

23a and 23b of the knob 24. In operation, the reversing mechanism is pressed forward and the

inner jaws

25a and 25b move to engage the

separator pins

510a and 510b, thereby moving the second first end drive wheel 484b away from the body back side 20 to engage a mating drive wheel (not shown). When the second first end drive wheel 484b and the mating drive wheel move in one direction they interlock and rotate the body, but allow the teeth to move past each other when they move in the opposite direction. The reversing mechanism is pressed rearwardly and the

outer jaws

25c and 25d move to engage the separator pins 510c and 510d, thereby moving the first end drive wheel 484a away from the body back side 20 to engage a mating drive wheel (not shown). When the first end drive wheel 484a and the counter drive wheel move in one direction they interlock and rotate the body, but when they move in the opposite direction the teeth are allowed to move past each other.

Fig. 27A and 27B are gear drive type compression ratchet wrenches 800. The geared compression ratchet wrench 800 of the present invention includes an upper housing 802 and a lower housing 804 that are assembled to form a drive wheel cavity 806 therebetween. A set of gears 808 is disposed within the drive wheel cavity 806. The set of gears 808 may include 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or

more gears

812a, 812b, 812c, 812d having different or similar pitches and different gear ratios. The set of gears 808 may also include a handle adapter gear 814 and a ratchet adapter gear 816 coupled to the set of gears 808 for coupling the first handle 818a and the drive adapter 820. In one example, the set of gears 808 includes four gears with peripheral teeth. Gear 812a includes a plurality of teeth around a circumference for engaging gear 812c, with gear 812b abutting gear 812a and contacting gear 812 c. Gear 8112c has a plurality of teeth that contact gear 812 d. Gear 812d is connected to ratchet adapter gear 816, which receives drive adapter 820 and may be secured with screws 822. The first handle 818a is attached to the adaptor gear 814. When the first handle 818a and the second handle 818b are pressed together, the first handle 818a rotates the handle adaptor gear 814, thereby rotating the set of gears 808. Thus, rotation of the first handle 818a causes the gear 812a to transmit the motion to the set of gears 808 and ultimately to the drive adapter 820 via the set of gears 808. The second handle 818b may be positioned on the upper housing 802, the lower housing 804, or both. The set of gears 808 are coupled to the second body 804 or positioned on an insert disposed on the lower housing 804, the upper housing 802, or both. The upper housing 802, the lower housing 804, or both, may have a second handle 818b that provides leverage to rotate the first handle 818 a. In operation, the first handle 818a and the second handle 818b are pressed together, thereby rotating the adapter gear 814, which rotates the set of gears 808, which in turn rotates the ratchet adapter gear 816, which houses the drive adapter 820. In addition, the ratchet adapter gear 816 includes a recessed aperture 824 that is shaped to receive the drive adapter 820. Other embodiments that include a ratchet adapter gear 816 may include a recessed aperture 824 shaped to receive a spline drive, square bit, polygonal bit, etc. (not shown).

Fig. 27B is a view of a geared compression ratchet wrench 800 having a pair of end face drive wheels. The geared compression ratchet wrench 800 of the present invention includes an upper housing 802 and a lower housing 804 that are assembled to form a gear cavity 806 therebetween. A set of gears 808 is disposed in the gear cavity 806. The set of gears 808 may include 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or

more gears

812a, 812b, 812c, 812d having different or the same pitch and different gear ratios. The set of gears 808 may also include a handle adapter gear 814 and a ratchet adapter gear 816 coupled to the set of gears 808 for coupling to a first handle 818a and a drive adapter 820, respectively. The handle adaptor gear 814 may include a set of face gears 826a, wherein the teeth 830 of the face gear set 826a are disposed on the top surface 828 of the handle adaptor gear 814 and the plurality of teeth 830 are disposed around the perimeter of the handle adaptor gear 814. The first handle 818a includes a set of mating face gears 826b that are disposed on a bottom surface (not shown) of a face gear insert (not shown) that is disposed around the positioning cylinder 834 such that the set of teeth of the face gears 826b are aligned. The set of gears 808 includes four gears with teeth on the periphery. Gear 812a is peripherally toothed to engage gear 812c, and gear 812b is placed on gear 812a to contact gear 812 c. Gear 812c has a plurality of teeth that contact gear 812 d. Gear 812d is connected to a ratchet adapter gear 816, which receives a drive adapter 820 and may be secured with screws 822. The first handle 818a is connected to the adaptor gear 814. When the first handle 818a and the second handle 818b are pressed together, the first handle 818a rotates the handle adaptor gear 814, thereby rotating the set of gears 808. Thus, rotation of the first handle 818a causes the gear 812a to transmit the motion to the set of gears 808 and ultimately to the drive adapter 820 via the set of gears 808. The second handle 818b may be positioned on the upper housing 802, the lower housing 804, or both. The set of gears 808 are coupled to the second body 804 or positioned on an insert disposed on the lower housing 804, the upper housing 802, or both. The upper housing 802, the lower housing 804, or both, may include a second handle 818b that provides leverage to rotate the first handle 818 a. In operation, the first handle 818a and the second handle 818b are pressed together to rotate the adapter gear 814, which rotates the set of gears 808, which in turn rotates the ratchet adapter gear 816, which receives the drive adapter 820. In addition, the ratchet adapter gear 816 includes a recessed aperture 824 configured to receive the drive adapter 820. Other embodiments that include a ratchet adapter gear 816 may include a recessed bore 824 configured to receive a spline drive, square bits, polygonal bits, etc. (not shown).

The set of gears 808 may have a variety of different configurations (increased gear ratio, decreased gear ratio, strength, size, etc.) depending on space constraints and the particular application. For example, a gear arrangement may be employed to provide for the increase or decrease in gear ratio. Engagement of gear teeth and gear arrangements may be used to allow for changes in torque and speed between an input value and an output value. For example, the combination of 8-tooth gears 8A, 8B, 8C and 40-tooth gears 40A, 40B, 40C results in a significantly reduced gear ratio. For example, the final gear ratio between 8-tooth gear 8A and 40-tooth gear 40A is 125: 1. This is achieved by combining 8-toothed gear 8A driving 40-toothed gear 40B, 8-toothed gear 8B driving 40-toothed gear 40C, and-8-toothed gear 8C driving 40-toothed gear 40A at a 5:1 ratio to convert the 100rpm input to a 0.8rpm output (conversion can also be accomplished by converting the 0.8rpm input to a 100rpm output). Another example includes a 40-tooth drive gear 40A coupled to an 8-tooth gear 8A to provide a 1:5 gear ratio, i.e., 1rpm for the drive gear 40A and 5rpm for the 8-tooth gear 8A. The 20-tooth drive gears 20A and 24-tooth gear 40B mesh with the 40-tooth drive gear 40A to provide gear ratios of 1:2 and 1:1.66, i.e., drive gear 40A rotates at 1rpm and gears 20A and 40B rotate at 2rpm and 1.66rpm, respectively.

Fig. 28A is a view of a driving type compression ratchet wrench 800 having a pair of end face drive wheels. The drive-type compression ratchet wrench 800 of the present invention includes an upper housing 802 and a lower housing 804 that are assembled to form a drive wheel cavity 806 therebetween. In operation, the first handle 818a and the second handle 818b are pressed together to rotatably drive the adapter 820. The first handle 818a and the second handle 818b are attached to different portions of the upper housing 802 and/or the lower housing 804, respectively. A set of drive wheels 808 is disposed within the drive wheel cavity 806. The description of the set of driving wheels 808 has been described with respect to one embodiment in fig. 19, 21 and 22. The set of drive wheels 808 may include 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or more gears having different or the same pitch and different gear ratios. The set of drive wheels may be connected to the lower housing 804 by a set of face drive wheels 826 disposed in the gear cavity 806, which cooperate with a set of face drive wheels (not shown) on the underside of the set of drive wheels 808. The set of drive wheels 808 are coupled to a dynamic adapter 820 that extends from the upper housing 802 and is positioned by the member 836. The set of face drive wheels 826 and the set of pair of face drive wheels (not shown) cooperate to allow the teeth (not shown) of the set of pair of face drive wheels (not shown) to pass over the teeth 830 on the set of face drive wheels 826 when rotated in one direction and to lock with one another when rotated in the opposite direction. A direction selection mechanism may be used in this embodiment (e.g., as in fig. 26). A biasing mechanism 838 can be disposed between the set of end face drive wheels 826 and the bottom surface of the lower housing 804 (e.g., the button mechanism of fig. 18 can also be incorporated into various embodiments as in fig. 18). In operation, the first handle 818a and the second handle 818b are pressed together, thereby rotating the set of end face drive wheels 826 and the set of pair of end face drive wheels (not shown) on the bottom surface of the set of drive wheels 808. As the pair of end face drive wheels (not shown) rotate, the set of drive wheels 808 are rotated and in turn rotate the drive adapter 820 extending from the upper housing 802.

Fig. 28B is a view of a driving type compression ratchet wrench 800 having a pair of end face drive wheels. The drive-type compression ratchet wrench 800 of the present invention includes an upper housing 802 and a lower housing 804 that are assembled to form a drive wheel cavity 806 therebetween. The drive wheel cavity 806 also has an alignment lever 838. In operation, the first handle 818a and the second handle 818b are pressed together to rotate the drive adapter 820. The first handle 818a and the second handle 818b are attached to different portions of the upper housing 802 and/or the lower housing 804, respectively. A set of drive wheels 808 is disposed within the drive wheel cavity 806. The set of drive wheels 808 includes a first end face drive wheel 840 having a first set of teeth 842 around the perimeter of the first end face drive wheel 840 and a set of first end face drive wheel face teeth 844 disposed on a top surface of the first end face drive wheel 840. The first end drive wheel 840 also includes a first end drive wheel alignment aperture 846. The set of drive wheels 808 includes a second end face drive wheel 848 having a set of second end face drive wheel end teeth 850 disposed on a bottom surface 852 of the second end face drive wheel 848. The second end face drive wheel 848 is connected to the second handle 818b such that movement of the second handle 818b rotates the second end face drive wheel 848. In fig. 28B, the second end face drive wheel 848 has a pair of shank pins 856 which fit into shank holes 858a and 858B of the second handle 818B. The second handle 818b also includes a handle alignment hole 860 that receives the alignment lever 838. The drive adapter 820 is positioned in the drive wheel cavity 806 by being disposed on a drive adapter post 862 fixed to the lower housing 904. The drive adapter 820 includes adapter teeth 864 that mesh with a first set of teeth 842 disposed on a periphery of a first end drive wheel 840. As the first end drive wheel 840 rotates, the circumferentially disposed first set of teeth 842 rotate the adapter teeth 864, thereby rotating the drive adapter 820. The set of second end face pulley face teeth 850 are aligned on a bottom surface 852 of the second end face pulley 848 with the set of first end face pulley face teeth 844 located on a top surface of the first end face pulley 840. The second end face pulley 848 also includes a second end face pulley alignment aperture 854. An alignment lever 838 is received in the first end drive wheel alignment aperture 846 to position the first end drive wheel 840 in the drive wheel cavity 806 such that the set of first end drive wheel end teeth 844 face upward from the drive wheel cavity 806. The second end face pulley 848 is positioned such that the set of second end face pulley face teeth 850 are aligned with the set of first end face pulley face teeth 844 by fitting the second end face pulley alignment aperture 854 and the alignment rod 838 together. In an alternative embodiment, the second handle 818b includes a second end face driver face tooth 850 for contacting the first end face driver 840. Similarly, the second end face drive 848 may be circular, oval, square, scalloped, or any other shape that provides tooth contact. The description of the set of drive wheels 808 has been described in one embodiment shown in fig. 19, 21 and 22. The set of drive wheels 808 may include 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or more gears having different or the same pitch and different gear ratios, and may also include a face-engaging gear with its teeth facing in opposite directions. As in any of the examples given herein, the gear ratios may be changed to any suitable ratio by changing the spacing, size, location, etc. of the gears and/or teeth, e.g., the ratios may be 1.5:1, 2.5:1, 3.5:1, 4.5:1, 5.5:1, 6.5:1, 7.5:1, 8.5:1, 9.5:1, 10.5:1, 1:1, 2:1, 3:1, 4:1, 5:1, 6:1, 7:1, 8:1, 9:1, 10:1, 11:1, 12:1, 13:1, 14:1, 15:1, 20:1, 25:1, 50:1, etc., which may be used in the opposite direction, or may be 50:1, etc.

Although the drive wheels described in the different embodiments give specific gear types, a person skilled in the art will appreciate that other types of drive wheels may be used. For example, cylindrical gears have tooth contact that is primarily rolling, with slippage occurring as the gears engage and disengage. The rack and pinion are essentially rectilinear variants of cylindrical gears. Internal ring gears include cylindrical gears with meshing teeth inside or outside the ring, often used in conjunction with cylindrical gears. The inner ring gear may be used in a planetary gear configuration. The helical gear comprises a cylindrical gear having helical teeth. The helical rack gear is linear in shape and cooperates with a rotating helical gear. The herringbone gears may have left-handed and right-handed helical teeth. The face gear is a disk body with one side cut with a circle of teeth. The gear teeth taper towards the tooth center. The worm gear teeth are similar to the meshing with the helical gear except that they envelope the worm as viewed along the worm axis. The double-enveloping worm gear has a pitch circle diameter that varies radially. This increases the number and size of the tooth shear zones. Straight bevel gears have tapered conical teeth that intersect with identical tooth shapes. Bevel gears are used to transmit motion between shafts where the centerlines intersect. The angle of intersection is typically 90 degrees but may be as high as 180 degrees. If the mating gears are the same size and the shafts are positioned at 90 degrees to each other, they are called miter gears. The teeth of the bevel gears can also be cut in a curved fashion, resulting in a spiral bevel gear that operates more smoothly and quietly than a straight cut tri-gear. The spiral bevel gear has spiral angle spiral teeth. Helical gears (crossed helical gears) are helical gears with opposite helix angles that mesh with crossed axes.

The sleeve joint may be configured to mount a sleeve of conventional size (e.g., 1/4, 1/2, 3/4, 1)¹/₄,1¹/₂,1³/₄,2,2¹/₄,2¹/₂,2³/₄3, etc.). Furthermore, the sleeve engagement can be configured as a spline transmission or face gear. The textured region of the handle may be formed in or disposed on the handle portion and constructed of rubber, plastic, metal, polymer, leather, wood, or other suitable material.

As used herein, the term "sleeve" refers to conventional sleeves, such as metric sleeves, stepped sleeves, long sleeves, short sleeves, chrome-plated sleeves or impingement sleeves, and the like, in the shape of a hex head, a dodecagonal head, a spline, a Torx star, and the like.

In this context, a number of examples can be composed and adapted for use in all types of wrenches, such as solid wrenches or solid wrenches: an integral wrench having a U-shaped opening clamps opposite sides of a bolt or nut. Such wrenches are typically double ended, with the openings at each end being of different sizes. The ends are often oriented at an angle of approximately 15 degrees relative to the longitudinal axis of the handle. This enables a large range of movement within the enclosed space by turning the wrench over; ring or socket wrenches (double-ended staggered): an integral wrench having a closed opening that clamps against multiple faces of a bolt or nut. The notches are typically hexagonal or dodecagonal openings for polygonal nuts or bolt heads. The twelve-cornered opening is mounted to the fastener at up to twice the angle, with the advantage that swing is limited. Octagonal wrenches are also manufactured for square nuts and bolt heads. Ring wrenches are typically double ended and typically have staggered handles for better access to the nut or bolt. Combination wrench or combination wrench: a double-ended tool, like a solid wrench or solid wrench at one end and a socket wrench or ring wrench at the other end, usually fits bolts of the same size at both ends. Taper nut wrench, pipe wrench or wire wrench: for clamping the nut at both ends of the tube. This type of wrench is similar to a socket wrench but does not fully encase the nut, it has a small opening but is wide enough to allow the wrench to be placed over the pipe. This allows maximum access to the vertical nut, which is typically a relatively soft metal and thus more susceptible to damage by solid wrenches; adjustable spanner/wrench, end adjustable spanner, adjustable wrench or adjustable spanner: open ended wrenches with adjustable (usually smooth) jaws; the adjustable wrench or the pneumatic clamp is an old type end adjustable wrench and is provided with a straight arm handle and a smooth jaw; pipe wrench: the end adjustable wrench is provided with a self-tightening performance and hard sawtooth-shaped jaws which only grab the soft iron pipe and the pipe joint; box spanner, universal joint and box spanner: a hollow cylinder, which may include a handle, but is typically used with a variety of driving tools, placed on one end of a nut or bolt head, and which typically has a hexagonal or dodecagonal notch, may be of the short or long sleeve type, and may have a built-in universal joint. The commonly used drive handles are: a bent (hinged) handle, also known as a connection nut wrench or a soft-head nut wrench, often referred to as a break-open bar. It is a long non-ratchet rod, break-in rods are often used for self-locking bolts and nuts. The extra length of the break-open bar allows the same amount of force to be applied to produce a force that is significantly greater than that which can be applied with a standard length ratchet wrench. Ratchet spanner: the wrench comprises a one-way mechanism which allows the sleeve to rotate without removing the sleeve from the nut and bolt, and only enables the wrench to move back and forth; a quick-action handle, a crank handle or a quick-action crank; a screwdriver handle: for use with a sleeve like a nut driver; breaking and detaching the rod: it is an elongated handle for a socket wrench that adds extra torque to unscrew a tightly screwed or stuck fastener. Torque wrench: a socket wrench drive tool that measures the amount of turning force applied to the socket, which can be visually indicated by a lever or scale, or simply slips when a set torque is exceeded. Torque wrenches are also classified as measuring tools; jaw (Crowfoot) socket wrench: a socket is designed to mount some of the same drive handles as conventional sockets, but is not cylindrical. Both ends are the same shape as both ends of a wrench, socket wrench or taper nut wrench. These sleeves are used in applications where space is limited where conventional sleeves cannot be used, and they are used in principle with torque wrenches. Torque (Saltus) wrench: a socket wrench is similar in design to a socket wrench in that a socket is permanently fixed to the handle, the socket is not as interchangeable as with a socket wrench, and the socket is often rotated about the handle to allow a user to access the fastener from different angles. Typically, the torque wrench is part of a double-ended wrench with the wrench head on the opposite side of the socket head. A socket wrench: a tube with 6-sided sleeves at both ends, which is rotated with a short rod (e.g., a turner rod or T-bar) inserted in two holes in the middle of the tube; impact/impact wrench: wrenches (both solid and ring wrenches) have a closed end to the handle, designed for use with hammers, often used for removing large nuts and bolts, where tapping vibrations is effective against damaged rust paint.

An allen wrench/socket for use with screws and bolts having an internal bore, comprising: allen wrench, hex socket wrench or L-socket allen wrench, typically L-shaped wrenches, made of hexagonal wire of different sizes, are designed for rotation with a hex recess to receive the wrench head or bolt head. Bristol wrench or Bristol spline wrench: another wrench designed for socket head screws and bolts has a cross-section similar to a square tooth gear, but is not of conventional design and is primarily intended for small screws. Torx star wrench: socket head screw designs, which are star-like in cross-section, are commonly used in the automotive industry, automation equipment and computer components because they are resistant to wrench bulge and are therefore suitable for use in power tools for all types of production line assembly. Strap or chain wrenches: a self-tightening wrench having a metal, leather, rubber chain or belt attached to a handle for gripping and rotating a smooth cylindrical object, such as an automobile oil filter. In the field of bicycle repair, it is known as a wrap chain and is primarily used to remove and install a cassette at the rear hub. Schematically showing how a pipe wrench allows a user to grasp square-head fasteners of different sizes. Pipe wrench: early wrenches of the type commonly used by mechanics, factory workers, and farmers for maintenance, repair, and operation in times when fasteners typically had square heads rather than hexagonal heads. The wrench shape suggests an alligator shape. Double-handle tap wrench, awl wrench: a particularly thin wrench for adjusting the inner race of a bearing on a hub. The front hub is usually 13 mm, and the rear hub is usually 15 mm. Spoke spanner or spoke spanner: the wrench has a clearance pocket for a wire spoke, such as a bicycle spoke, and a drive head for adjusting the nipple nut. A tap wrench: a dual shank wrench is used to turn a square drive on a tap in a tapping operation (e.g., cutting a female thread on a nut) or precision reaming bit. A die wrench: a double-handled wrench for rotating dies (e.g., cutting male threads on bolts) in a tapping operation. Barrel wrenches, also known as "barrel wrenches," are tools commonly used to open large 55 gallon barrels. A cross wrench: a socket wrench for rotating a tire nut onto a vehicle wheel. Pipe wrench: a tool for screwing (forcibly turning) various pipes during lead sealing. Tuning spanner: socket wrenches for tuning certain stringed instruments. Oil filter spanner: a wrench for removing a cylindrical oil filter, which may be a band wrench or a socket. A water tank wrench: a self-tightening wrench, also known as a basin wrench, is mounted on one end of a torque tube with a cross-handle at the opposite end for tightening the fitting of a drain valve of a wash basin in a ceramic sink, such a nut being normally placed deep in a recess and the self-tightening head of which can be turned over to loosen the fitting. Punch wrench or mini punch: a steel frame installation tool includes a conventional wrench at one end and a sharp nail at the other end for aligning bolt holes (typically in the case of mating two pipe flanges), often referred to in the united states as a long handle wrench. Golf shoe spike spanner: a T-shank wrench having two pins and a gap for a shoe spike allows the shoe spike to be inserted into and removed from the shoe. Cover head nut spanner: a flat wrench having a circular bore and two inwardly projecting pins is used to engage a slot in a nut used on a bicycle to secure a front fork pivot bearing to a frame rail. Fire hydrant wrench (hose coupling): the hose connector has a threaded ferrule that includes a male pin. The end of the wrench handle has an arcuate bend for engaging the pin. Fire hydrant wrench (valve operator): such a pentagonal (pentagonal) type socket wrench avoids the use of a hexagonal shape for the lobes so that the valve is not damaged, wherein the opposing faces are not parallel. Illegal opening of the hydrant is almost impossible because the person who wants to open does not have a suitable tool.

In addition to mechanical direction selection and disengagement mechanisms, the present invention also employs a magnet mechanism to select direction, select gears, engage or disengage one or more gears. Many permanent magnets may be used in the present invention, such as rare earth magnets, ceramic magnets, Alnico (Alnico) magnets, which may be rigid, semi-rigid, and flexible magnets. The flexible magnet is made by doping a flexible material such as chloroprene rubber, vinyl, nitrile, nylon or plastic with a magnetic material such as magnetic iron pieces, which will be used in the present invention.

Other examples for use as described above are rare earth magnets, including neodymium iron boron (NdFeB) and samarium cobalt (SmCo) type magnets. Within each category there are multiple levels, which have a wide variety of performance and application requirements. Rare earth magnets are available in sintered and bonded form.

The ceramic magnet is a sintered permanent magnet made of barium ferrite (BaO (Fe)₂O₃) Sub.n) or tin ferrite (SnO (Fe)₂O₃)_n) Wherein n is a variable of the number of ferrites. Also known as anisotropic hexaferrite, this type of magnet is useful because of its good demagnetization resistance and low cost. Although ceramic magnets tend to be hard and brittle and require special machining techniques, these magnets can be used in very precise gauge magnetic retention mechanisms. The anisotropy levels are oriented in manufacture and must be magnetized in a particular direction. Ceramic magnets may also be isotropic, and are generally more practical due to lower cost. Ceramic magnets may be used in many applications and may be prepackaged or formed for use in the present invention.

A flexible magnet is a magnet constructed of a material that is flexible and bonded to a magnetic material. Flexible magnets provide product designers with a unique combination of desirable properties at low cost. The materials that are flexible and incorporate magnetic compositions have the advantage that they can be bent, twisted, crimped, die stamped and otherwise machined into almost any shape without loss of magnetic field. Under normal operating conditions, the use of flexible magnets is desirable because they do not require coatings, are corrosion resistant, are easy to process, are easy to handle, can be compounded with magnetic materials having high magnetic energy.

More expensive magnet materials such as rare earth magnets can be coated onto flexible backing materials such as plastics, nylon and polypropylene and will have excellent magnetic strength and flexibility. In addition, the flexible magnet can be made very thin, for example 1/18 inches or less in thickness.

The flexible magnet may also be attached to the magnetic retention mechanism of the present invention by an adhesive suitable for various environments. The type of adhesive used to bond the flexible magnets will depend on the particular application, for example the adhesive may be pressure sensitive. The magnets may be laminated with, for example, a pressure sensitive adhesive. The adhesives used in the present invention are known to those skilled in the art.

Alnico magnets are mainly made of alnico and are characterized by excellent temperature stability, high residual magnetic flux density and relatively high energy. Alnico magnets are manufactured by casting or sintering. Cast magnets can be manufactured to very high specifications and can have very specific shapes. Sintered alnico magnets are slightly less magnetic than cast magnets, but have higher mechanical properties.

Alnico magnets are very corrosion resistant. Although alnico magnets are easily demagnetized, this problem can be overcome with simple operational instructions. Alnico magnets have the advantage that the temperature has little influence on their magnetic properties.

In addition, the present invention can be used in both clockwise and counterclockwise directions. Specifically, the pawl may be used to select either clockwise or counterclockwise rotation by selecting the knob to move the pawl to engage the gear and limit rotation in the opposite direction. In other embodiments, dogs may be used to disengage a gear set to limit movement. Magnets may also be used instead of dogs to engage a set of gears or to disengage a gear or set of gears. Additionally, magnets and jaws may be used in combination as a redundant system or as an engagement mechanism. In other embodiments gear teeth are provided around the gear rim and the pawl is selectively engaged to the teeth.

The present invention provides a set of drive wheels for transmitting torque, comprising: an upper drive wheel having an at least partially textured upper drive wheel face; at least one double-sided intermediate drive wheel, each intermediate drive wheel including an at least partially textured intermediate gear first side on an opposite side of an at least partially textured intermediate drive wheel second side, the intermediate drive wheel first side configured to engage the at least partially textured upper drive wheel face; a lower drive wheel including an at least partially textured lower drive wheel face configured to engage the at least partially textured second intermediate drive wheel second face to transmit torque from the upper drive wheel to the lower drive wheel. The drive wheel set is adapted to be mounted in the cavity of the ratchet wheel and the at least partially textured upper drive wheel face, the at least partially textured intermediate drive wheel first face, the at least partially textured intermediate drive wheel second face, and the at least partially textured lower drive wheel face each independently can include a splined face, a ribbed face, a stepped face, a textured face, a wavy face, an undulating face, a twill face, a striated face, a grooved face, a meshing face, a toothed face, a peened face, a smooth face, a rough face, a sticky face, or other suitable surface that allows friction between the surfaces. The drive wheel set may comprise at least one double-sided intermediate drive wheel comprising 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or more gears, the one or more double-sided intermediate gears comprising a first set of one or more intermediate drive wheels stacked on a second set of one or more double-sided intermediate drive wheels. The drive train may be provided in a ratchet, socket wrench, coupling assembly, right angle connector or similar device. The gear set can be operably disposed in an automobile, motorcycle, bus, truck, train, aircraft, boat, ship, watercraft, bicycle, cart, golf cart, dolly, recreation horse car, transmission, linkage, transmission case, differential, overdrive, drive shaft, turbine, windmilling, pulley, winch, harness, manipulator, drill, saw, construction equipment, hoisting machinery, compressor, crown block, grinder, winch, watch, copier, tie down tool, 0-90 degree angled connection for tools, and other components having gears.

While the present invention has been described with reference to exemplary embodiments, the description herein is not intended to be construed in a limiting sense. Various modifications and combinations of the illustrative embodiments, as well as other embodiments of the invention, will be apparent to persons skilled in the art upon reference to the description. It is therefore intended that the appended claims encompass any such modifications or embodiments.

It is contemplated that any embodiment described in the specification can be practiced with any method, device, reagent, or composition of the invention, and vice versa. In addition, the compositions of the invention can be used to implement the methods of the invention.

It will be understood that the specific embodiments described herein are shown by way of example and not as limitations of the invention. The main features of the invention can be used in various embodiments without departing from the scope of the invention. Those skilled in the art will recognize, or be able to ascertain by routine experimentation, many equivalents to the specific procedures described herein. Such equivalents are considered to be within the scope of this invention and are covered by the claims.

All publications and patent applications mentioned in the specification are indicative of the level of skill of those skilled in the art to which this invention pertains. All publications and patent applications are herein incorporated by reference to the same extent as if each individual publication or patent application was specifically and individually indicated to be incorporated by reference.

The terms "a" and "an" when used in conjunction with the term "comprising" in the claims and/or the specification mean "single," but also correspond to "one or more," at least one, "" one, or more than one. The term "or" in the claims means "and/or" unless explicitly indicated to mean only two or the two are mutually exclusive, although the disclosure supports definitions only representing two and "and/or". Throughout this application, the term "about" is used to describe a value that includes inherent variations in the error of the apparatus and the method used to determine the value, or variations that exist in the subject.

As used in the specification and claims, the terms "comprises" (and any form thereof, such as a single plural number thereof), "has" (and any form thereof, such as a single plural number thereof), "comprises" (and any form thereof, such as a single plural number thereof), or "comprises" (and any form thereof, such as a single plural number thereof) are inclusive or open-ended and do not exclude additional, unrecited elements or method steps.

As used herein, the term "or combinations thereof refers to all permutations and combinations of the items listed prior to that term. For example, "A, B, C or a combination thereof" is intended to include at least one of: a, B, C, AB, AC, BC, ABC. If order is important in a particular context, BA, CA, CB, CBA, BCA, ACB, BAC or CAB is also included. Following this example, combinations comprising one or more repeats are expressly included, such as BB, AAA, AAB, BBC, AAABCCCC, BBAAA, CABABB, and the like. Those of skill in the art will understand that there is generally no limitation on the number of items or terms in any combination, unless otherwise clear from the context.

All of the compositions and/or methods described and claimed herein can be made and executed without undue experimentation in light of the present disclosure. While the compositions and methods of this invention have been described in terms of preferred embodiments, it will be apparent to those of skill in the art that variations may be applied to the compositions and/or methods, in the steps of the methods, or in the sequence of steps of the methods described herein without departing from the concept, spirit and scope of the invention. All such similar substitutes and modifications apparent to those skilled in the art are deemed to be within the spirit, scope and contemplation of the invention as defined by the following claims.

Claims

1. A manual hoist having a drive multiplier mechanism, comprising:

a first drive wheel housing;

a handle extending from the first drive wheel housing;

a second drive wheel housing matching the first drive wheel housing;

a lifting rod extending from the second transmission wheel housing;

a seat connected to the first drive wheel housing, the second drive wheel housing, or both to provide a base;

a limiting mechanism for fixing the first transmission wheel shell to the second transmission wheel shell;

a gear cavity formed between the first drive wheel housing and the second drive wheel housing;

a gear set disposed within the gear cavity, the gear set including a ring gear having a set of inner ring teeth disposed in an inner bore of the ring gear fixed to the first drive wheel housing; two or more planet gears having one or more teeth that contact the set of inner ring teeth of the ring gear; a central sun gear disposed between the two or more planet gears to contact the one or more teeth; and a link connected to the central sun gear and fixed to the second drive wheel housing, wherein rotation of the handle causes the ring gear to rotate which in turn rotates the two or more planet gears and the central sun gear, thereby moving the lifter bar such that the handle rotates the lifter bar at a multiple of its rotational speed.

2. A manual hoist as claimed in claim 1, wherein the two or more planetary gears include 3, 4, 5, 6, 7, 8, 9, 10 or more planetary gears.

3. A manual hoist as claimed in claim 1, wherein the two or more planetary gears are circular or elliptical in shape.

4. A manual hoist as claimed in claim 1, wherein the multiple is 0.1, 0.2, 0.3, 0.4, 0.5, 0.6, 0.7, 0.8, 0.9, 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or more.

5. An adjustable rotational multiplier extension mechanism comprising:

a first drive wheel housing having a first opening for gripping;

a second drive wheel housing secured to the first drive wheel housing, wherein the second drive wheel housing has a second adapter on an opposite side of the first opening;

a ring gear fixed in the first drive wheel housing, the ring gear having a set of inner ring teeth disposed in an inner bore of the ring gear;

two or more planet gears contacting the set of inner ring teeth of the ring gear;

and two or more planet gears are positioned to allow an interchangeable connecting gear with a first adapter connected to the central sun gear to be inserted and removed, the first adapter extending through the first opening, wherein rotation of the second adapter causes the ring gear to rotate, thereby rotating the two or more planet gears and the central sun gear, such that the first adapter rotates at a multiple of the rotational speed of the second adapter.

6. The multiplication extension mechanism of claim 5, wherein the first adapter, the second adapter, or both are configured to receive a driving tool.

7. The multiplication extension mechanism of claim 5, wherein the second adapter is configured to receive 1/4, 1/2, 3/4, 1 drive tools.

8. The multiplication extension mechanism of claim 5, wherein the first adapter, the second adapter, or both are configured to receive a sleeve.

9. The multiplication extension mechanism of claim 5, wherein the first adapter is configured to receive a sleeve and the second adapter is configured to receive a driving tool.

10. The multiplication extension mechanism of claim 5, further comprising a direction selection mechanism contacting one or more of the two or more planet gears, the central sun gear, and the ring gear.

11. The multiplication extension mechanism of claim 5, wherein the two or more planetary gears include 3, 4, 5, 6, 7, 8, 9, 10 or more gears.

12. The multiplication extension mechanism of claim 5, wherein the two or more planetary gears are circular or elliptical.

13. The multiplication extension mechanism of claim 5, wherein the multiple is 0.1, 0.2, 0.3, 0.4, 0.5, 0.6, 0.7, 0.8, 0.9, 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or more.

14. The multiplication extension mechanism of claim 5 wherein the first drive wheel housing includes a textured area around the exterior for gripping.

15. An adjustable rotational multiplication adapter comprising:

a first driving wheel housing having an upper opening for gripping;

a second drive wheel housing secured to the first drive wheel housing, the second drive wheel housing having a second adapter on the opposite side of the upper opening;

a central sun gear aperture disposed between two or more planet gears to accommodate a plurality of removable central sun gears; and

a plurality of removable and replaceable couplings including a spline gear for engaging the two or more planet gears and a first adapter connected to the central sun gear and extending through the upper opening, wherein rotation of the second adapter causes rotation of the ring gear which in turn causes rotation of the two or more planet gears and the central sun gear, whereby the first adapter rotates at a multiple of the rotational speed of the second adapter.

16. The multiplication adapter of claim 15, wherein the plurality of removable central sun gears each include a spline gear at a first end for engaging the two or more planet gears and a first adapter of a different size at a second end for receiving a sleeve.

17. The multiplication adapter of claim 15, wherein the removable central sun gear includes a spline gear at a first end for engaging two or more planet gears and a sleeve at a second end.

18. The multiplying adapter of claim 15 wherein said second adapter is configured to receive a driving tool.

19. The multiplying adapter of claim 15 wherein said second adapter is configured to receive a drive tool of 1/4, 1/2, 3/4, 1.

20. The multiplying adapter of claim 15 wherein said first adapter is configured to receive a sleeve.

21. The multiplication adapter of claim 15, wherein the first adapter is configured to receive 1/4, 1/2, 3/4, 1 drive sleeves.

22. The multiplication adapter of claim 15, further comprising a direction selection mechanism contacting one or more of two or more planetary gears, the central sun gear and the ring gear.

23. The multiplying adapter of claim 15 wherein said two or more planetary gears comprise 3, 4, 5, 6, 7, 8, 9, 10 or more gears.

24. The multiplying adapter of claim 15 wherein said two or more planetary gears are circular or elliptical in shape.

25. The multiplying adapter of claim 15, wherein the multiple is 0.1, 0.2, 0.3, 0.4, 0.5, 0.6, 0.7, 0.8, 0.9, 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or more.

26. The multiplying adapter of claim 15 wherein the first drive wheel housing includes a textured area about an exterior for gripping.