Rotary impact device

Abstract

The present invention provides methods and systems for a rotary impact device having an annular exterior surface for use with an impact wrench for providing torque to a fastener. The rotary impact device includes an input member having an input recess for receiving the anvil of the impact wrench, an output member having an output recess for receiving the fastener, and an inertia member. The inertia member is stationary and positioned on the exterior surface of the rotary impact device for increasing the torque applied to the fastener.

Claims

1. An impact tool, comprising: an impact tool that includes a rotary hammer and an anvil; wherein the hammer impacts the anvil to rotate the anvil; wherein the anvil extends outwardly from the hammer; a socket that secures to the anvil opposite the hammer; wherein the socket includes a body that extends between a first end and a second end: wherein the first end includes a first opening having a first inner wall that extends inwardly from the first opening to define a square-shaped input recess that receives the anvil to secure to the anvil opposite the hammer; wherein the second end includes a second opening and a second inner wall that extends inwardly from the second opening to define a hexagonal-shaped output recess configured to receive a head of a fastener; wherein the body includes a cylindrical outer surface that defines a first radius; wherein the body includes a disk positioned between the first end and the second end and a distance closer to the first end than to the second end; wherein the disk defines a second radius that is greater than the first radius, wherein the disk includes at least two ribs extending outwardly from the cylindrical outer surface; wherein a ring is secured to an outer radial end of each rib and is spaced apart from cylindrical outer surface; wherein the disk remains stationary with respect to the body including the first end and the second end and located exterior of the impact tool.

2. The impact tool of claim 1, wherein the body of the socket is formed as a single monolithic steel body.

3. The impact tool of claim 1, wherein the ring has an inner surface that defines a third radius extending from the body, the third radius being greater than the first radius and less than the second radius.

4. An impact tool, comprising: an impact tool that includes a rotary hammer and an anvil; wherein the hammer impacts the anvil to rotate the anvil; wherein the anvil extends outwardly from the hammer of the impact tool; a socket that secures to the anvil opposite the hammer; wherein the socket includes a body that extends between a first end and a second end, the body including: wherein the first end includes a first opening having a first inner wall that extends inwardly from the first opening to define a square-shaped input recess that receives the anvil to secure to the anvil opposite the hammer; wherein the second end includes a second opening and a second inner wall that extends inwardly from the second opening to define a hexagonal-shaped output recess configured to receive a head of a fastener; wherein the body includes a cylindrical outer surface that defines a first radius; wherein the body includes a disk positioned between the first end and the second end; wherein the disk includes a first ring that extends transversely from the body to a second radius that is greater than the first radius of the outer surface of the body; wherein the disk includes at least two ribs extending outwardly from the second radius of the first ring to a third radius; wherein a second ring is secured to an outer radial end of each rib and is spaced apart from first ring.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The present invention is illustrated and described herein with reference to the various drawings, in which like reference numbers denote like method steps and/or system components, respectively, and in which:

(2) FIG. 1 is a perspective view of one embodiment of the rotary impact device;

(3) FIG. 2 is a another perspective view of the rotary impact device of FIG. 1;

(4) FIG. 3 is a cut-away view of the rotary impact device of FIGS. 1 and 2;

(5) FIG. 4 is a partial cut-away side view of an impact wrench that may be used with the rotary impact device;

(6) FIG. 5 is a graph charting the torque vs. socket inertia of a prior art socket and the rotary impact device of the present invention to determine the optimized inertia;

(7) FIG. 6 is a perspective view of another embodiment of the rotary impact device;

(8) FIG. 7 is a perspective view of another embodiment of the rotary impact device;

(9) FIG. 8 is a block diagram indicating a standard prior art socket disposed on the anvil of an impact wrench for removing a fastener; and

(10) FIG. 9 is block diagram of the present invention indicating an inertia member that adds a substantial mass a large distance from the axis of rotation of the rotary impact device.

DETAILED DESCRIPTION OF THE INVENTION

(11) Referring now specifically to the drawings, an improved rotary impact device is illustrated in FIG. 1 and is shown generally at reference numeral 10. The device 10 may be attached to and driven by an impact tool that is a source of high torque, such as an impact wrench 12. The device 10 is intended to be selectively secured to the impact wrench 12. The device 10 is preferably made of steel.

(12) As illustrated in FIGS. 1, 2, and 3, the device 10 has an annular exterior surface and comprises an input member 14, an output member 16, and an inertia member 18. The input member 14 comprises an input recess 20 that extends partially along the axial direction of the device 10. Preferably, the input recess 20 is generally square shaped and is designed to be selectively secured to the anvil 22 of an impact wrench 12. However, other polygonal shapes may also be used. The anvil 22 includes a round body with a generally square drive head. The generally square drive head is designed to be received within the input recess 20 for forming a selectively secured arrangement.

(13) The output member 16 includes an output recess 26. As illustrated in FIG. 1, the output recess 26 is a polygonal-shaped output recess 26 for receiving a fastener. The output recess 26 extends partially along the axial direction of the device 10. The fastener may be a bolt, screw, nut, etc. As is well known within the art, at least a portion of the fastener (e.g. the head of a bolt and the body of a screw) has a polygonal-shape that corresponds with the polygonal-shaped output recess 26. During use, the polygonal-shaped portion of the fastener is inserted into the polygonal-shaped output recess 26 for operation and is selectively secured to one another by friction fit. The fastener is preferably hexagonally shaped.

(14) The inertia member 18 is substantially circular and is positioned on the exterior surface of the device 10. Preferably, the inertia member 18 is disposed on the exterior surface of the device 10 nearest the input member 14. However, the inertia member 18 may be disposed on any portion of the exterior surface of the device 10 as desired by the user. The inertia member 18 is preferably positioned so as to not interfere with the engagement of the input member 14 to the anvil 22 and the engagement of the output member 16 to the fastener.

(15) The device 10 is designed to be engaged to an impact wrench 12. As is well known by one of ordinary skill in the art, an impact wrench 12 is designed to receive a standard socket and designed to deliver high torque output with the exertion of a minimal amount of force by the user. The high torque output is accomplished by storing kinetic energy in a rotating mass, and then delivering the energy to an output shaft or anvil 22. Most impact wrenches 12 are driven by compressed air, but other power sources may be used such as electricity, hydraulic power, or battery operation.

(16) In operation, the power is supplied to the motor that accelerates a rotating mass, commonly referred to as the hammer 28. As the hammer 28 rotates, kinetic energy is stored therein. The hammer 28 violently impacts the anvil 22, causing the anvil 22 to spin and create high torque upon impact. In other words, the kinetic energy of the hammer 28 is transferred to rotational energy in the anvil 22. Once the hammer 28 impacts the anvil 22, the hammer 28 of the impact wrench 12 is designed to freely spin again. Generally, the hammer 28 is able to slide and rotate on a shaft within the impact wrench 12. A biasing element, such as a spring, presses against the hammer 28 and forces the hammer 28 towards a downward position. In short, there are many hammer 28 designs, but it is important that the hammer 28 spin freely, impact the anvil 22, and then freely spin again after impact. In some impact wrench 12 designs, the hammer 28 drives the anvil 22 once per revolution. However, there are other impact wrench 12 designs where the hammer 28 drives the anvil 22 twice per revolution. There are many designs of an impact wrench 12 and most any impact wrench 12 may be selectively secured with the device 10 of the present invention.

(17) The output torque of the impact wrench 12 is difficult to measure, since the impact by the hammer 28 on the anvil 22 is a short impact force. In other words, the impact wrench 12 delivers a fixed amount of energy with each impact by the hammer 28, rather than a fixed torque. Therefore, the actual output torque of the impact wrench 12 changes depending upon the operation. The anvil 22 is designed to be selectively secured to a device 10. This engagement or connection of the anvil 22 to the device 10 results in a spring effect when in operation. This spring effect stores energy and releases energy. It is desirable to mitigate the negative consequences of the spring effect because the device 10 utilizes the inertia generated by the inertia member 18 to transmit energy past the connection of the anvil 22 and the device 10. Additionally, there is a spring effect between the device 10 and the fastener. Again, this spring effect stores energy and releases energy. It is again desirable to mitigate the negative consequences of the spring effect because the device 10 utilizes the inertia generated by the inertia member 18 to transmit energy past the connection of the device 10 and fastener.

(18) The purpose of the inertia member 18 is to increase the overall performance of an impact wrench 12, containing a rotary hammer 28, by increasing the net effect of the rotary hammer 28 inside the impact wrench 12. The performance is increased as a result of the inertia member 18 functioning as a type of stationary flywheel on the device 10. Stationary flywheel means the flywheel is stationary relative to the device 10, but moves relative to the anvil 22 and the fastener. By acting as a stationary flywheel, the inertia member 18 increases the amount of torque applied to the fastener for loosening or tightening the fastener.

(19) In a prior art application, a standard socket is disposed on the anvil 22 of an impact wrench 12 for removing a fastener, as indicated in FIG. 8. It should be noted that FIG. 8 is shown in a linear system, but the impact wrench 12 and socket is a rotary system. The mass moment of inertia of the impact wrench 12 is designated m.sub.2 and represents the mass moment of inertia of the rotary hammer 28 inside the impact wrench. The spring rate of the anvil 22 and socket connection is represented by k.sub.2. The spring rate of the socket and fastener connection is represented by k.sub.1, and the fastener is represented by ground. As represented in FIG. 8, the combined spring rate of k.sub.1 and k.sub.2, greatly reduces the peak torque delivered by the impact wrench 12 during impact with the fastener. The combined spring rate of k.sub.1 and k.sub.2 allows the mass m.sub.2 to decelerate more slowly, thereby imparting a reduced torque spike.

(20) In the present application, as illustrated in FIG. 9, the inertia member 18 adds a substantial mass a large distance from the axis of rotation of the rotary impact device 10. Again, it should be noted that FIG. 9 is shown in a linear mode, but the impact wrench and socket is a rotary system. The inertia member 18 of the rotary impact device 10 is represented by m.sub.1. The inertia member m.sub.1 is situated between spring effects k.sub.1 and k.sub.2. The spring rate of the anvil and socket connection is represented by k.sub.2. The spring rate of the socket and fastener connection is represented by k.sub.1, and the fastener is represented by ground. The mass moment of inertia of the impact wrench is designated m.sub.2 and represents the mass moment of inertia of the rotary hammer inside the impact wrench. The spring rate of k.sub.1 is three times that of k.sub.1 and k.sub.2 combined, causing very high torques to be transmitted from the inertia member m.sub.1 to the fastener.

(21) As is known to one of ordinary skill in the art, the combination of two masses (m.sub.1 and m.sub.2) and two springs (k.sub.1 and k.sub.2) is often referred to as a double oscillator mechanical system. In this system, the springs (k.sub.1 and k.sub.2) are designed to store and transmit potential energy. The masses (m.sub.1 and m.sub.2) are used to store and transmit kinetic energy. The double oscillator system can be tuned to efficiently and effectively transfer energy from the impact device (m.sub.2) through k.sub.2, inertia member (m.sub.1) and k.sub.1 and into the fastener. Proper tuning will ensure most of the energy delivered by the impact wrench m.sub.2 is transferred through spring k.sub.2 and into the inertia member 18. During use, the rate of deceleration of mass m.sub.1 is very high since spring k.sub.1 is stiff. Since deceleration is high the torque exerted on the fastener is high.

(22) The preexisting elements of the double oscillator system are predetermined. The rotary hammer inside the impact wrench m.sub.2 and springs k.sub.1 and k.sub.2 have defined values. For tuning the system, the only value which needs to be determined is the inertia member m.sub.1 (18) of the rotary impact device 10 for achieving optimized inertia. The impact wrench, depending upon the drive size (i.e. , , 1), has a different optimal inertia for each drive size. The spring rate k.sub.2 and the rotary hammer inside the impact wrench m.sub.2 are coincidentally the same for all competitive tools. As illustrated in FIG. 5, the optimal inertia for a drive impact wrench is charted by comparing the performance torque with the socket inertia. A standard socket is charted and the rotary impact device is charted in FIG. 5. As is clearly evidenced in FIG. 5, the rotary impact device 10 of the present invention has a higher torque output than a standard, prior art socket. Additionally, the optimized inertia for a drive impact wrench is 0.0046 lb-ft.sup.2 (1.938 kg-cm.sup.2).

(23) The inertia member 18 may have any configuration that would increase the torque output of the rotary impact device 10. One exemplary embodiment of the inertia member 18 is illustrated in FIGS. 1 and 2. The inertia member 18 has a front surface 30, a top surface 32, and a back surface 34. In this exemplary embodiment, the inertia member 18 contains three-spaced apart bores 36 that extend substantially longitudinally along the inertia member 18. In other words, the three-spaced apart bores 36 extend along the front surface 30 and back surface 34. The three spaced-apart bores 36 extend through the inertia member 18 from the front surface 30 to the back surface 34. The transition from the front surface 30 of the inertia member 18 contains a chamfer 38 that circumscribes the spaced apart bores 36. Although three-spaced apart bores 36 are illustrated in FIG. 1, any number of spaced apart bores 36 may be utilized, or in the alternative, the inertia member 18 may be a solid piece containing no bores 36.

(24) Additionally, the output member 16 contains a beveled outer edge 40. The beveled outer edge 40 allows for easily inserting the fastener into the output recess 26 of the output member 16. When the output member 16 comes in contact with the fastener for forming a selectively secured arrangement, the beveled outer edge 40 of the output recess 26 aids in guiding the fastener into the output recess 26.

(25) Another exemplary embodiment of the rotary impact device is shown in FIG. 6 as is referred to generally as reference number 110 including an output member 116. The inertia member 118 of this exemplary embodiment has a ring 142, which may be solid, containing three (3) ribs 144 for keeping the ring 142 stationary and engaged to the exterior surface of the device 110. The three ribs 144 are engaged to the exterior surface of the device 110 for positioning the ring 142 in a spaced apart relationship with the device 110. The ribs 144 extend radially outward from the exterior surface of the device 110 and include a collar 146 prior to the rib 144 engaging the ring 142. The rib 144 extends slightly beyond the front surface 130, top surface, 132, and back surface 134 of the ring 142 forming a step 148 upon these surfaces (130,132,134) of the ring 140.

(26) Another exemplary embodiment of the rotary impact device is shown in FIG. 7 and is referred to generally as reference number 210 including an output member 216. The inertia member 218 of this exemplary embodiment is a ring 242 containing five (5) ribs 244. The ribs 244 keep the ring 244 stationary and engaged to the exterior surface of the device 210. The five (5) ribs 244 are engaged to the exterior surface of the device 210 for positioning the ring 244 in a spaced apart relationship with the device 210. The ribs 244 extend radially outward from the exterior surface of the device 210 and include an inset 250 within the interior of each rib 244. A shelf 252 is positioned on the front surface 230 of the ring 242 for receiving each rib 244. Likewise, a shelf 252 may be positioned on the back surface 234 of the ring 242 for receiving each rib 244.

(27) Although the present invention has been illustrated and described herein with reference to preferred embodiments and specific examples thereof, it will be readily apparent to those of ordinary skill in the art that other embodiments and examples may perform similar functions and/or achieve like results. All such equivalent embodiments and examples are within the spirit and scope of the present invention and are intended to be covered by the following claims.