US2408228A

US2408228A - Impact tool mechanism

Info

Publication number: US2408228A
Application number: US523694A
Authority: US
Inventors: Carroll H Richards
Original assignee: Individual
Current assignee: Individual
Priority date: 1944-02-24
Filing date: 1944-02-24
Publication date: 1946-09-24
Anticipated expiration: 1963-09-24

Description

Sept. 24, 1946; c. H; RICHARDS IMPACT TOOL MECHANISM Filed Feb. 24, 1944 .3 Sheets-Sheet l aw i iifg P 1946- c. H. RICVHARDS 2,408,228

IMPACT TOOL MECHANI SM Filed Feb. 24, 1944 3 Sheets-Sheet 2 v 1NVENTOR.' {864M 21k, M d-f A Sept. 24, 1946- c. H. RICHARDS IMPACT TOOL MECHANISM a Sheets-Sheet s Filed Feb. 24', 1944 INVEN'I'Q ii: 4 44 [624mm Patented Sept. 24, 1946 UNITED STATES PATENT-i FFICE,

I Carroll H. Richards, Boston, Mass. I v Application February 24, 1944, Serial No. 523,694

This invention relates to impact tool mechanisms, such as impact wrenches.

6 Claims. (oi-192 305) .witliparts of the motor and ho us ing broken away.

In previous impact mechanisms with which I have been familiar, the hammer is decelerated on impact with the driven element. In the mechanism of the invention, a rotating hammer is accelerated and is capable of delivering a, greater driving force to the driven member. This is a great advantage because it provides greater force when needed most. v

The deceleration of the impact hammer in previous impact tool mechanisms necessarily causes the motor driving the mechanism to slow down, or stop, between impacts, and heretofore the only motor that would perform satisfactorily under these conditions has been 'a pneumatic or compressed-air motor. An impact tool embodying the present invention, however, is capable of being driven by an electric motor, as Well as by compressed air. This is a great advantage'in operations where compresed air is not readily available.

Furthermore, in prior impact tool mechanisms the hammer surface becomes quickly distorted and deformed through constant hammering, and.

the same angle of contact between the hammer and anvil faces at all times is impossible. These machines vary in performance, quickly lose their efficiency, and parts must be frequently replaced.

In my mechanism, however, positive means are provided for maintaining the same angle of impact at all times for greatest efiiciency and constant performance, despite wear. r

A further important object of the present invention is to provide an impact tool mechanism which will absorb the reaction of the impact within itself.

Another advantage of the present tool lies in the provision of auxiliary means to dampen or smooth out the revolutions of the mechanism to reduce vibration and jerkiness in operation.

Before explaining in detail the present invention it is to be understood that the invention is not limited in its application to the details of construction and arrangement of parts illustrated in the accompanying drawings, since the invention is capable of otherembodiments and of being practiced or carried out in various ways. Also it is to be understood that the phraseology or terminology employed herein is for the purpose of description and not of limitation, and it is not intended to limit the invention claimed herein beyond the requirements of the prior art.

In the drawings: r Fig. 1 is a sectional view of an impact wrench,

of Fig. w r

Fig; .3 is asectional view taken on line 3 -3 ofFig.1.

"Fig. 3a is' a detail end view, of the rotatable torque receiving member D, shown in'Figs. 1,.2

and3. 1 1,, Fig- 4.is a sectional view of another form of construction of the rotatable torque receiving member with partof itshousing and other parts broken away. V

Fig. 5 is an end view of the rotatable torque receiving member shown in Fig. 4. q I

. Fig. 6 is a, section of the rotatable torque re- .ceiving member taken on line 66 of Fig. i.

Fig. 7 is a, plan view'of one of the parts of the rotatable torque receiving member shown in Fig. 4. Fig. 8 isa side elevation of the driving element. Fig-9 is a side elevation of the driven element. Fig. 10 is a perspective view of the driving connection between the rotatable torque receiving member and the driven element. I I q Fig. 11 is a perspective view of a special gear constitutingthe driving connection between the rotatable torque receiving member and the driving element. y

Figs. 12 to 19 inclusive are diagrams showing the relation of'certain of, the parts at difierent periods in the operation of the device, taken from Fig. 2 is arsectionalview taken on line 2-2 the point of view of the operator using the deof Fig. 1, and opposite to anism of the invention which housing is made in two parts, upper part B and lower part K, conventionally fitted'together and held in place by bolts and nuts 40 .(Fig. 1). Spindle A of the driving power unit is journaled in ball bearing l0 conventionally held in partition ll located in the upper portion Bof the housing. It is understoodthata suitable motor, pneumatic, electric, or otherwise (not shown), provides power for driving spindle A. The splined end [2 of spindle A fits into splined hole l3 of the driving element C, and the driving force is transmitted by spindle A through these splines to the driving element C. The end I4 of driving element C abuts one end of ball bearing l0 and aids in locating the ball bearing. Driving element C (Figs. 1, 2 and 8) includes the flanged portions I 5, having two gear teeth 7 spaces It therein and extending from the center 3 shaft portion 11, at the extreme end of which is another shaft portion l8, smaller in diameter than portion IT.

A rotatable torque receiving member D (Figs. 1, 3 and 3a) is rotatably mounted on driving element C about shaft portion 11, having a central hole [9 into which shaft portion l1 fits.

Two driving connections E (Figs. 1, 2 and 10) having shaft portions are rotatably mounted in holes or bearings 29 and 30 of the rotatable torque receiving member D (Figs. 1 and 3a), said holes 29 and 36 being located a, suitable distance out from the center of the rotatable torquereceiving member D. Shaft portion 20 has splines 2| at one end, and an annular groove 22 adjacent the splines 21 adapted toreceive a conventional spring fastening ring 32 (Fig. l). Splined on the splined ends of driving connection-E are specially designed acceleration control parts H.(Figs. 1, 2 and 11), each having one tooth 3i. Gear teeth 3i operate in gearspaces l6 of driving element C and receive the driving force therefrom. The contacting surfaces of these gear teeth 3| are arcuate surfaces and their radius R (Fig. 2) may be changed to suit different operating conditions. The spring rings 32 fitting in the annular grooves 22 on splined ends 2! of driv ing connection E aid in locating parts. H on the splined end 2! of shaft portion 20 and prevent longitudinal movement of the parts H in one direction along shaft portion 20.

At the opposite end of shaft portion 2%! of driving co nection E. and integral with it. is hammer head F (Figs. 1, 3 and 10), having

hammer faces

23 and 24 forming a V, the open ends of the V terminating in

rounded noses

25 and 26 adapted to contact a cylindrical surface guide (3%). The V-shaped hammer faces facilitate the transmission of the drive in either direction. Cylindrical surface portions 21 and 28, opposite

rounded noses

25 and 25 respectively, on hammer head F slidably contact inner cylindrical surface 55 of guide ring G (Figs. 1 and. 3), and maintain the proper angle of impact for hammer faces 23 and 24 at all times. Guide ring G is suitably located and fastened in the lower portion K of the housing.

Driven element I (Figs. 1', 3 and 9) is rotatably mounted in bearing 33 located and held in lower portion K of the housing. Cylindrical end portion 34 of driven element I, having central cavity 36 therein, receives the smaller shaft portion l8 of the driving element C, and serves as a bearing for shaft portion l8, and as a lubricant reservoir. Cylindrical end portion 34 has two anvil faces of inverted V-shape. oppositely located thereon. adapted to receive the impact of hammer faces 23 and 24 of hammer head F (Fig. 3)., and to drive driven element I in either direction around shaft portion l8 of driving element C. Rounded

noses

25 and 23 of the hammer heads F on the driving connections E, ride the cylindrical surface 34 of driven element I when not contacting the anvil faces 35 and aid in guiding hammer heads F of driving connection E, to insure the correct angle of impact atfthe exact instant of impact of hammer faces 23 and 24, with the cooperating anvil faces 35 of driven element I.

menjtC, in driving contact itransmits the drive to the socket or wrench 3'3 which is adapted to receive bolt heads, nuts, studs, or other resisting element to be turned.

The operation of my device is as follows: After fitting the socket or wrench 33 over the bolt or other head to be tightened, the motor is started and this rotates in a clockwise direction, as viewed from the left, the position of the operator using the wrench (Fig. l). Spindle A' of the motor which has splined driving connection with driving element 0, imparts the drive to driving element (3. The surfaces of gear teeth spaces it of driving elewith gear teeth if of parts Hin turn transmit the drive to the parts I i, Whichbeing splined to end 2! of the driving con: nections E, transmit the drive thereto, and thence to hammer heads F,-which are integral parts of driving connections E.

Assuming that the parts are in the positions shown in FigalS and 3.9, the hammer heads F and the torque balancer D rotate a whole with the driving element C andat the speed of the "drive, until the hammer faces 23of hammer heads F. contact the cooperatinganvil faces of the driven element I.

After the hammer faces 23 have made contact with the cooperative anvil faces 35, if the ratio of the driving torque transmitted through the hammer faces 23 to the anvil faces35, to the resisting torque transmitted at the anvil faces 35 from driven element L is substantially the same, then the driving element C, the rotatable torque receiving memberD, parts H, driving connections E, and the driven element I, will all rotate as 'a whole at the same speed as the driving element C, with substantially no relative movement between the parts moving as a whole (Figs. 12 and 13).

v However, if after the hammer faces 23 have made contact with the anvil faces 35 and driving torque transmitted through the hammer faces 23 to the. anvil faces 35 is less than the resisting torque transmitted to the anvil face-s 35 from the driven element I, the operation then is as follows: The rotatable torque receiving member D re sponds to this torque ratio by being accelerated faster than the. drive, causing hammer heads F to be turned or rockedin a clockwise direction (from the position. of the operator using the wrench) and thus disrupting the driving contact between hammer faces 23 of hammer heads F g and the cooperating anvil faces 35 of the driven The shank 37 of driven element I revolves in 1 bearing 33 which serves as both a radial and' thrust bearing. At the extreme end of shank 31 of driven element I is a non-circular, preferably square portion 3,8 that receives the conventional socket or Wrench 39, rigidly mounted thereon in any suitable manner. End portion 38, of course,

element I, and'the driven element remains at rest (Figs. 14 and 15).

After the disruption of the drive, driving element C, parts H, driving connections E, and rotatable torque receiving member D, all rotate about central shaft if for aninterval, during which, through the cooperative functions of the guides, (cylindrical surface 3 3. of driven element I, andtheinner cylindrical surface 55 of ring G acting on the rounded noses 25 or arcuate' surface portion 28, respectively, of the hammer heads F), the driving connections are forced by the drive into potential driving relations (Figs. 12,13, 18'and 19). The said interval of driving required to force the driving connection-s into potential driving relations depends on the design, application and type of driving power, and usually never exceeds (sixty-five degrees) of a revolution. After the driving connections have been forced by the drive into potential driving relations, the driving element C, torque balancer D and hammer heads F allrotate as a unit until the hammer faces 23 of the hammer heads F, contact the anvil faces 35 of the driven element I, and substantially at this instant, an impact is delivered and the torque balancer D is accelerated and the driving connection between the hammer faces 23 and the anvil faces 35 then is disrupted as previously described.

The driven element I transmits the drive through its end portion 38 to the conventional socket or wrench 39; which drives the head 'of the nut, bolt, or'other resisting element being turned, and impacts occur at successive intervals until the bolt is suiliciently tightened, or otherwise turned, or the operator terminates the operation at any time. It is obvious from the foregoing that the driven element I is driven at the same speed as the driving element C when the ratio of the driving torque to the resisting torque is substantially the same, and that when the resisting torque is greater thanthe driving torque, because of the resistance encountered, the driven element I is driven at intervals by successive impacts and forces due to the acceleration of the rotatable torque receivingmember D.

Fig. 12 shows the relative positions of the gear teeth 3! of parts H, to the contacting surfaces l6 of the tooth spaces of 'the driving element C, at the time of impact, or when the entire mechanism is being driven as a whole with substantially no relative movement between the component parts of the mechanism. Fig. 13 shows the corresponding relative positions of the hammer faces 23 of driving connections E to the anvil faces 35 of the'driven element I, and inner cylindrical surface 55 of guide ring G at the same period as in Fig. 12. Here hammer faces 23 are in driving contact with the cooperating anvil faces 35 of the driven element I, rounded noses 25 of the hammer heads F are in contact with surfaces 34 of the driven element I, being,

forced into this position by the driving force imparted through driving element C to gear teeth 3! of parts H. I

Fig. 14 shows the relative position of gear, teeth 3| of parts H to their cooperative contacting surfaces |6 of the driving element 0, just after im pact, or at, or near the beginning of the full disruption of the drive. r

Fig. 15 shows the relative position between hammer head F and driven element I at the same period as in Fig. 14, with hammer surfaces 23 of hammer head F in contact with the cooperating anvil surfaces 35 at practically one point. i

The angle made by the broken line OM in Fig. 14 and full line OP represents the angle through which the drivingelement C could have rotated from its impact position or driving position shown in Fig. 12. And the angle made by the vertical center line passing through center of rotation O and the dot and dash line OS represents the minimum angle th rotatable torque receiving member D could travel since the time of impact. It is obvious from the magnitude of these two angles, that the rotatable torque receivin member D has rotated more than twice as fast as the driving element C, during the time that was required for the driving element to rotate through the small angle MO-P. But the comparison of the magnitude of these angles does not disclose the maximum acceleration of the rotatable torque receiving member D, since member D had begun to slow down before it reached its point of travel disclosed in Figs. 14 and 15 and its acceleration was greater at the instant of contact disclosed in Figures 12 and 13. This slowing down of the rotatable torque receiving member D will b more apparent in the next step of the operation disclosed inFigs. l6 and 17.

Fig. 16 shows the positions of the gear teeth 3| of parts H relative to contacting surfaces l6 of the driving element C, at practically the point of total disruption of the drive. Fig. 17 shows the positions of the hammer heads F relative to the driven element C at the same period as in Fig. 16. In the position shown in Fig. 16 the driving element C has the maximum mechanical advantage to cause parts H to turn or rock the driving connections E in their bearings 29 and 30 in rotatable torque receiving member D, since the contacting surfaces I6 of driving element C, contact the teeth 3| of parts H at the farthest possible points from the centers of parts H. The purpose of designing the tooth to secure this condition is. that at this point in the operation,the drive begins to force the driving connection E into potential driving relations which is accomplished by the turning or rocking parts H about their own axis, which in turn rotate driving connections E and their hammer heads F, such that the rounded noses 26 of hammer heads F are moved to contact guiding surface 34 of the driven element I, or the arcuate surfaces 23 of the hammer heads F are moved to contact inne cylindrical surface 55 of the guide ring G.

Fig. 17 discloses the hammer head-F of the driving connection E tilted or rocked at its greatest possible angle about its own axis and ina clockwise direction, or at the point inits operation where it changes its direction of rotation or rocking and thereafter can rotate only in a counterclockwise direction about its own axis. At this point in the operation, guide of hammer heads F may be'obtained from any one of three surfaces, from rounded noses 25 of hammer heads F contacting the rounded apex of anvil surfaces 35 of driven element I, rounded noses 26 of hammer heads F contacting cylindrical surface 34 of driven element I, and arcuate surface 28 of ham mer heads F by contacting inner cylindrical surfaces 55 of guide ring G.

Fig. 16 shows the relative positions of gear teeth 3| of parts H to the contacting surfaces [6 of the driving element C. It is obvious by comparison of the relation of the parts disclosed in Figs. 16, 12 and 14 relative to their rotation about the center of rotation of the driving element C, that the average speed of the rotatable torque receiving member D (on which parts H and driving connection E aremounted) and the driving element C have been almost the same between the twopoints'of operation represented by Figs. 14 and 16 and that the rotatable torque receiving member D has slowed down to almost the speed of the driving element 0.

Fig. 18 shows the relative position of gear teeth 3| of parts H and contacting surfaces is of driving element 0 after the total disruption of the drive, and the driving connections are in normal potential driving positions. Fig. 19 shows hammer heads F at the same period as in Fig. 18. -Rounded noses 25 of hammer heads F are now riding the cylindrical guiding surface 34 of driven element I, and arcuate surfaces 21 of the hammer heads F arein sliding contact, or close to proxiinity of sliding contact, with'the inner cylindrical surface 55 of guide ring G. It is obvious from the relation of the parts disclosed in Figs. 18 and 19 that at this point in the operation that the driving element 0 and the rotatable torque'receiving member D are rotating at the same'speed. The relative positions of the gear teeth 3| of parts H to the contacting surfaces It of the driving elements C are the same in both Figs. 12 and 18;

From the drawings, it will be seen that the device is readily reversible, by reversing the direction of the power drive. When a reversal of the drive is required, to secure smoothness of operation, hammer heads F should start to rotate first about their own axis, before the actual driving or rotation of the rotatable torque receiving member D starts to rotate about the center of rotation of the driving element C. This is accom-:

plished by designing the teeth 3| of parts H such that the maximum mechanical advantage is had by the contacting surfaces of the tooth spaces l of the driving element 0, with contact of the gear teeth 3| as far from the center of rotation of the parts H as possible. As stated before, the

advantage of starting the rotation of parts H about their own axis, is to force as quickly as possible the driving connections into potential driving relation, and this is accomplished primarily by the rotation of parts 1-1.

It should also be apparent from the foregoing description that the rotatable torque receiving member D absorbs the reaction to the impact by its acceleration and this reaction is not transmitted to the housing or case of the impact wrench and thence to the operators hands. For instance, if the rotatable torque receiving member D were given a push applied at its periphery manually, or otherwise, to cause its rotation before driving contact with the driven element I was had, and the driving connections E could turn in their bearings 29 and 3 3 in the rotatable torque receiving member, that when the hammer faces 23 or 24 of the hammer heads F contacted the cooperating anvil faces of the driven element I, (assuming that the hammer heads F would be in potential driving relation at the time of contact), rotatable torque receiving member D would have to rotate faster than it was rotating at the time of impact or contact to cause a disruption of the drive.

The angle made at the apex of the intersecting surfaces of the anvil portion 35, is a factor in determining the acceleration of the rotatable torque receiving member D. If a constant speed of the driving element is had, the smaller the said angle,

the greater the acceleration and the greater the impact.

In the slowing down of the rotatable torque receiving member D and generally stabilizing its rotation, the arcuate surfaces 21 and 28 of the hammer heads F, which are adapted to slidably contact the inner surface of guide ring G, function similarly to the damper mechanism used in gasoline motor constructions to produce smooth performance. These arcuate surfaces 21 and 28 operate as a mild brake, until the instant of impact, when their contact with the inner cylindrical surface 55 of guide ring G, is instantaneously broken. The

rounded noses

25 and 26 of the hammer heads F, contacting the cylindrical surface 34 of the driven element I, function to some extent like the arcuate surfaces 21 and 28 of the hammer heads F, sliding over the inner cylindrical surface of guide ring G.

Since the speed of the motor, the mass of the rotatable torque receiving member, and the angle made by the surfaces of the anvil faces 35 in great part determine the magnitude of the impact, and since all these can be varied to suit conditions, and since the rotatable torque receiving member D is accelerated and there is no mass to be accelerated again to the motors speed after each impact, it will be apparent that a correct relative prolportioning can readily be had of the vital parts, and hence that the impact wrench disclosed can be made for almost any type of driving power, and satisfactory performance can be obtained therefrom.

Figs. 4, 5, 6 and 7 disclose a modification of the invention, in which the rotatable torque receiving member D is made in two parts 4| and 42. The object of this construction is to secure two bearings in the rotatable torque receiving member D, for each driving connection E, such that the hammer heads F, integral with the driving connections E have a bearing contiguous to each of their sides longitudinally along the shaft portions 2%), hammer heads F being located between the shaft ends 20, of the driving connections E. This construction is particularly desirable for heavy duty wrenches.

Part 4| of rotatable torque receiving member D (Figs. 6 and 7) has an extending arcuate segment 43, portions of which function similarly to the jaws of a jaw clutch and abut similar portions 44 of part 42 of member D. Arcuate lips d5 of portions 43 fit tight over arcuate projections 45 of part 42 and locate the parts centrally. The parts 4| and 42 are press-fitted together and are further held in place by rods 4! which extend through holes 48 of part 4| and holes 49 of part 42. Heads 59 of rods 41 (Figs. 5 and 6) contact part 42, and the other ends of rods 4'! each have an annular groove, into which fits a conventional spring fastening ring 5| contacting part 4|. The parts 4| and 42 are thus held together as practically one solid part.

The driven element I is elongated comparably to driven element I of Fig. 1 in order that part 42 of rotatable torque receiving member D may revolve about it. A bushing 52 (Figs. 4 and 6) is conventionally located in part 42 of rotatable torque receiving member D and functions as a bearing between a portion of the driven element 1 and rotatable member D.

Shaft portion II of driving element C, fits in hole IQ of part 4| of the rotatable torque receiving member D, and the member D is free to rotate about shaft portion l1.

Smaller shaft portion H5 in turn fits into cavity $5 of driven element 1 which acts as a bearing for shaft portion I8. Shaft portions 23 of driving connections E fit into bearings 29 and 38, formed in rotatable torque receiving member D, and are free to rotate thereon.

Hammer heads F are integral with driving connections E and are free to operate in apertures of the rotatable torque receiving memher I), and the hammer faces 23 and 24' (not shown) of the contacting heads F are adapted to contact anvil faces 35 of the driven element I through these apertures 53.

Parts H are splined to shaft portions 28, and teeth 3|, operate in gear teeth spaces iii of driving element C exactly as in the form shown in Fi .1.

I claim:

1. In an impact tool in combination, a rotatable driving member, a rotatable driven member having an impact receiving surface, a driving connection between said driving and driven members including a force receiving member rotatably mounted to rotate relative to said members, a hammer rotatably carried by said force receiving member and having an impact applying surface adapted torimpactlsaid receiving surface, said impact applying and impactreceiving surfacesat the time fof impact being positioned with respect to the axis of rotation of said hammer so that alinenormal to their engaging surfaces at any point: of the entirefportion thereof passes in back of said axis ,with respect -to the direction of rotation of ,the driving mem er whereby, when the forceKresisting movement of the driven member exceeds the force tending to drive said driven member said force receiving member is moved faster than said driving member in the direction of rotation of the driving member and the hammer is rotated in one direction about its axis to disrupt its driving connection with said impact receiving surface, said driving connection also including means for causing said hammer to rotate in the opposite direction when said driving connection has been disrupted, said last mentioned means including a member operatively connected with said hammer and contacting a driving surface on said driving member, and guide means for controlling the extent of rotation of said hammer in said opposite direction to locate the impact applying surface thereon in a predetermined position relative to said impact receiving surface.

2. In an impact tool, in combination, a rotatable driving member, a rotatable driven member having an impact receiving surface, a driving connection between said driving and driven members including a rotatably mounted hammer'having an impact applying surface adapted to impact said impact receiving surface, said driving connection also including means for causing said hammer to rotate in the direction of rotation of the driving member to disrupt said d'riving connection in response to the resultant component of force applied to said force applying surface at the time of impact of said surfaces, when the force resisting movement of the driven member exceeds the force tending to drive said driven member, all lines normal to said impact applying surface, at the time of impact being posi tioned behind the axis of rotation of said hammer with respect to the direction of rotation.

of said driving member.

3. In an impact tool, in combination, a rotatable driving member, a rotatable driven member having an impact receiving surface, a driving connection between said driving and driven members including a rotatably mounted hammer having an impact applying surface adapted to impact said impact receiving surface, said driving connection also including means for causing said hammer to rotate in the direction of rotation of the driving member to disrupt said driving connection in response to the resultant component of force applied to said force applying surface at the time of impact of said surfaces, when the forceresisting movement of the driven'member exceeds the force tending to drive said driven member, all lines normalto said im-,

pact applying surface, at the time of impact being positioned behind the axis of rotation of said hammer with respect to the direction of rotation of said driving member, said driving connection also including means for causing said hammer to rotate in the opposite direction to that of the driving member, when said driving connection has been disrupted, and guide means for controlling the extent of rotation of said hammer in said opposite direction to locate the impact applying surface thereon in a predetermined position relative to saidimpact receiving surface.

. .4. In an impact tool,'in combination, a rotatable driving -member, a rotatable driven member having an impact receiving surface, a driving connection between said driving and driven members'comprising a rotatably mounted hammer having'an impact applying surface adapted to impact said impact'receivingsurface, said driving connection also including means for causing said hammer to rotate in the direction of rotation of the driving member to disruptsaid driving connection in response to the resultant component of the force applied to said force applying surface at the time of impact of said surfaces, when the force resisting movement of the driven member exceeds the force tending to drive said driven member, said driving connection also including means for causing said hammer to rotate in the opposite direction to that of the driving member when said driving connection has been disrupted and guide me'ans'including inner and outer cylindrical surfaces and in which the inner Q end of said impact applying surface is provided having an impact receiving surface, a driving force receiving member for rotation about an with a rounded nose adapted to engage the inner' guide surface and in which the hammer is provided with a cylindrical surface adapted to engage the outer guide surface.

5. In an impact'tool, in combination, a rotatable driving member, a rotatable driven member connection between said driving and driven members comprising a force receiving member rotatably mounted to move relatively to said driving and driven members, a shaft mounted in said force receiving member for rotation about an axis spaced'radially outward from theaxisof rotation of said force receiving member, a hammer secured to said shaft to rotate therewith and having an impact applying surface adapted to impact said impact receiving surface, all lines normal to said impact applying surface at the time of impact being positioned behind the axis of rotation of said hammer with respect to the direction of rotation of said driving member whereby the resultant component of the force resisting movement of said driven member applied to said impact applying surface at the time of impact, causes said force receiving member to be moved faster than the driving member and in the same direction and said hammer is rotated in the same direction to disrupt said driving connection when the force resisting movement of the driven member is greater than the driving force applied to the driven member.

6. In an impact tool, in combination, a rotatable driving member, a rotatable driven member having an impact receiving surface, a driving connection between'said driving and driven members comprising a force receiving member rotattbly mounted to move relatively to said driving and driven members, a shaft mounted in said axisspaced radially outward from the axis of rotation of said force receiving member, a hammer secured to said shaft to rotate therewith and having an impact applying surface adapted to impact said impact receiving surface, all lines normal to said'impact applying surface at the time of impact being positioned behind the axis of rotation of said hammer with respect to the direction of rotation of said driving member, whereby the resultant component of the force resisting movement of said driven member applied to said impact applying surface at the time of impact,

11 causes said force receiving member to be moved faster than the driving member and in the same direction and said hammer is rotated in the same direction to disrupt said driving connection when the force resisting movement of the driving memher is greater than the driving force applied to the driven member, said driving connection also including a member secured to said shaft and having a curved surface adapted to slidably en- 12 gage a radially extending surface on said driving member whereby said hammer is rotated in the opposite direction when said driving connection is disrupted and guide means for controlling the extent of rotation of said hammer in said opposite direction to locate the impact applying surface thereon in a predetermined position relative to said impact receiving surface.

CARROLL H. RICHARDS.