US3463246A - Rotary percussive power tool with changeable drive - Google Patents

Description

2 Sheets-Sheet 1 mm we G INVENTOR He//na Qro/maffwna/m S- JM ATTORNEY H. BRONNERT Aug. 26, 1969 Romy rsncussrvn roman AT001l wma CHANGEABLE DRIVE Filed Dec. 27. 1967 v AU@ 25, 1969 H. BRONNERT 3,463,246

ROTARY PERCUSSIVE POWER TOOL WITHCHANGEABLE DRIVE 2 Sheets-Sheet 2 Filed Dec. 27. 1967 Fig. 2

INVENTOR ATTORNEY United States Patent O M Int. Cl. E21c 3/04;B25d 9/04, 9/06 U.S. Cl., 173-47 20 Claims ABSTRACT F THE DISCLOSURE A power tool wherein the barrel of a housing accommodates a cylinder which is reciprocable axially in respouse to rotation of the output shaft of a motor and thereby turns back and forth a sleeve which is held in the housing against axial movement and transmits torque to a first clutch element which is biased against a second clutch element. The latter can rotate in one direction an axially mova'ble tool holder which can be shifted axially of the housing to place its anvil into the range of reciprocatroy movement of a ram which is movable axially with and relative to the cylinder. The holder can accommodate tools which are rotatable therewith or are held against rotation by a suitably conligurated portion of the housing. The first clutch element is automatically disengaged from the second clutch element when the latter offers excessive resistance to rotation in the one direction.

Background of the invention The present invention relates to power tools in general, and more particularly to improvements in implements of the type which can be used to rotate and/ or to transmit axially oriented impacts to boring, drilling, chiseling or like tools.

In certain presently known power operated implements, the work-engaging tool is rotated in one direction in response to dissipation of energy by helical springs which also serve to prevent rotation of the tool in the other direction. The springs are likely to break when the tool offers excessive resistance to rotation and, if the bias of such springs is too strong, the implement is likely to break and to cause injury to the operator or to persons standing nearby. If the bias of springs is too weak, the usefulness of the implement is limited because the user is unable to drive a tool into or to remove material from a relatively hard or tough workpiece. Such implements are disclosed, for example, in German Utility Model No. 1,928,513.

It is also known to provide a power operated implement with a pneumatically actuated impact transmitting unit which strikes against one end of the tool. Such implements are disclosed, for example, in German Utility Model No. 1,196,608 and their drawback is that the transmission which is employed to rotate the tool is too bulky, too expensive and prone to malfunction. The tool is rotated continuously.

Summary of the invention It is an object of my invention to provide a simple, rugged and inexpensive power tool or implement which can transmit to a material-penetrating or material-removing tool torque and/ or axially oriented impacts in a novel and improved way.

Another object of the invention is to provide an implement wherein the tool can be rotated stepwise and wherein the user of the implement can determine the magnitude of impacts which are transmitted to the tool.

A further object of the invention is to provide an im- Patented Aug. 26, 1969 ICC plement which can be used solely as a means for effecting stepwise rotation of a tool or solely as a means for transmitting to the tool a series of axially oriented impacts of variable magnitude.

An additional object of the invention is to provide an implement wherein the tool receives impacts only at such times when it does not receive torque, or vice versa.

A concomitant object of the invention is to provide an implement wherein the tool is automatically disengaged from the torque transmitting means when it offers excessive resistance to rotation and wherein the exact resistance at which the transmission of torque ceases can be changed at the option of the user.

Still another object of the invention is to provide an implement wherein the parts which guide and support the impact transmitting means are protected against excessive wear and/ or breakage.

A further o'bject of the invention is to provide an mplement which can embody an electrically operated or fluid operated prime mover.

Another object of the invention is to provide a novel driving assembly which can effect intermittent axial and/ 0r rotary movements of a tool.

A further object of the invention is to provide la novel clutch which can transmit torque from the dri-ving assembly to the holder of a material penetrating and/or material removing tool.

An additional object of my invention is to provide an implement which can be operated by semiskilled persons, which is not likely to cause injury to the user or damage to a workpiece, and which can stand long periods of use and is more efficient than the aforediscussed conventional implements.

The improved implement comprises a housing, a driver assembly mounted in the housing and reciprocable axially in response to motion received from an electric or fluid-operated prime mover, a tubular member rotatably mounted in the housing, coupling means preferably comprising mating steep threads provided on the driver assembly and on the tubular member to turn the latter back and forth in response to reciprocation of the driver assembly, disengageable clutch means including a first element connected for rotation with the tubular member, a second element rotatable in the housing, and biasing means for urging one of the elements against the other element so as to maintain teeth provided on the one element in mesh with complementary teeth provided on the other element and to permit the teeth to move apart if the second element offers excessive resistance to rotation with the first element, and an axially movable tool holder connected for rotation with the second element and having an impact receiving portion or anvil movable into the range of the driver assembly so that a tool which is mounted in the holder can be rotated by the latter if it is non-rotatably secured thereto, that such tool can be moved axially in response to i-mpacts transmitted to the holder if the latters anvil is placed into the Irange of the driver assembly, or that the tool is rotated during intervals between successive impacts against the anvil.

The novel features which are considered as characteristic of the invention are set forth in particular in the appended claims. The improved power tool itself, however, both as to its construction and its mode of operation, together with additional features and advantages thereof, will be best understood upon perusal of the following detailed description of certain specific embodiments with reference to the accompanying drawing.

Brief description of the drawing FIG. 1 is a fragmentary axial sectional view of a portable power tool which embodies my invention;

FIG. 2 is an enlarged transverse sectional view as seen in the direction of arrows from the line II-II of FIG. l;

FIG. 3 is an enlarged developed view of a portion of a clutch in the power tool of FIG. 1;

FIG. 4 is an enlarged transverse sectional view as seen in the directional of arrows from the line IV-IV of FIG. 1;

FIG. 5 is a fragmentary side elevational view of a first tool which can be used in the structure of FIG. 1; and

FIG. 6 is a similar fragmentary side elevational view of .a second tool.

Description of the preferred embodiments FIG. l illustrates a portion of a portable power tool comprising a housing 1 having a pistol grip type handle 5 which accommodates a suitable prime mover whose rotary output shaft is shown at 7. The latter drives a single-stage step-downtransmission 2 which serves to convert rotary movement of the shaft 7 into reciprocatory movement of a driver assembly 3. The handle 5 has an actuatingmember 6 e.g., an electric switch or a valve actuator, depending upon whether the prime mover is an electric motor or a fluid-operated motor.

Thetransmission 2 includes a pinon 7a which can form an integral part of the output shaft 7 and meshes with agear 8 mounted on ashaft 10 which is journalled in the housing 1. Thegear 48 is provided with aneccentric pin 9 for .a roller 9a extending into a transverse slot in acarriage 11 which forms part of the driver assembly 3 and is reciprocable inways 12 provided in the Irear portion of the housing 1. The arrangement is such that thecarriage 11 reciprocates along theways 12 in response to rotation of the output shaft 7. The driver assembly 3 further includes anelongated cylinder 13 which is threadedly connected with thecarriage 11 and has a larger-diameter intermediate portion slidable in abearing sleeve 17 of the housing 1. Thecylinder 13 accommodates the rear end portion orpiston 14a of van impeller orram 14 whose stem orrod 14b is slidably guided in and can extend forwardly beyond the smaller-diameter front end portion of the cylinder. Thepiston 14a divides the interior of thecylinder 13 into two air-filledchambers 15, 16 wherein the bodies of air act not unlike cushions to prevent the ram from striking with excessive force against thecarriage 11 and/or against the shoulder between the median and front end portions of thecylinder 13. The latter is provided with one or more substantially centrally locatedairow restricting openings 18 which can admit air to thechambers 15, 16 in order to compensate for eventual leakage -when theram 14 moves back and =forth.

The front end portion of thecylinder 13 is provided with a set of steepexternal threads 19 meshing with internal threads 20 of a tubular member or sleeve 21 which turns back and forth in response to reciprocation of the cylinder but is held against axial movement by thebearing sleeve 17 and housing 1 (the rear portion of the sleeve 21 has one or more outwardly extendingprojections 22 which bear against the front end face of thebearing sleeve 17 and against an internal shoulder of the housing 1) as well as by anannular socket 23 which is mounted in the housing in such a way that it cannot move axially. The common axis of thecylinder 13 and of the barrel of the housing 1 is shown at 24. Thethreads 19, 20 form a simple coupling which converts axial movements of the driver assembly 3 into rotary movements of the sleeve 21. The external surface of the sleeve 21 is formed with axiallyparallel splines 25 receiving internal ribs provided on a ring-shaped clutch element 26 which forms part of a clutch 4. Thus, theclutch element 26 is movable axially with reference to the sleeve 21 but cannot rotate thereon. Aprestressed clutch spring 27 is inserted between the projection orprojections 22 and theclutch element 26 to bias the latter forwardly toward the working end of the power tool.

As shown in FIG. 3, the front end face of theclutch element 26 is formed with an annulus of saw teeth 28 l 1 4 each having a substantially axially extendingank 28a Yand a more pronouncedlyinclined flask 28b. Theflanks 28a, 28b of eachtooth 28 make an acute angle. A second orcomplementary clutch element 30 of the clutch 4 hascomplementary saw teeth 29 which normally mesh with theteeth 28 in a manner as shown in FIG. 3. Theclutch element 30 is threadedly connected with thesocket 23, i.e., the latter can be considered as forming part of the clutch elementv 30 or vice versa. Thesocket 23 is rotatable on anannular insert 31 of the housing 1 and hasinternal splines 32 for external ribs provided on atool holder 33 which is movable therein in the axial direction of the housing. Therear portion 34 of theholder 33 constitutes an impact receiving anvil and can be struck by thestem 14b of theram 14 when the latter performs a forward stroke. 'Ihe front portion of theholder 33 is formed with aflange 35 located in front of acentral portion 36 whose diameter exceeds the diameter of the ribbed rear end portion. A prestressedhelical spring 37 is inserted between thesocket 23 andcentral portion 36 to bias theholder 33 forwardly so as to normally maintain theflange 35 in abutment with aninternal stop surface 38 provided on thefront end portion 39 of the housing 1. As shown in FIGS. l and 4, thefront end portion 39 of .the housing 1 accommodates a transversely extendingretaining bolt 41 which is mounted inelastic bearing rings 42. The peripheral surface of thebolt 41 has a flat 41b which can be moved into parallelism with theaxis 24. To this end, thebolt 41 is connected with a manuallyoperable yoke 41a which, when moved to the position shown in FIG. 1, holds the flat 41b in a plane which is normal to theaxis 24. When the at 41b is parallel with this axis, the operator can insert into the hexagonal bore 40 of thefront end portion 39 the shank of a drilling orboring tool 43 shown in FIG. 5. The shank is also provided with a flat so that it can bypass thebolt 41 when the at 41b is parallel to theaxis 24. FIG. 5 shows that the drilling orboring tool 43 is provided with ashank 45 of square cross-section outline. Theshank 45 can extend into thecomplementary bore 46 of theholder 33 so that the tool of FIG. 5 is compelled to rotate with theclutch element 30 when the latter receives torque from theclutch element 26. A smaller-diameter portion 44 of thetool 43 is engaged by thebolt 41 when the latter assumes the position shown in FIG. 1 and thus holds the tool against ejection from thefront end portion 39 of the housing 1. FIG. 6 shows achisel 43A whoseshank 47 is round and amedian portion 48 of which is hexagonal so that it is non-rotatably receivable in the hexagonal bore 40 of thefront end portion 39. Thus, thetool 43A of FIG. 6 can be moved axially but cannot rotate with theholder 33. Theportion 48 has a depression 44' which receives a portion of thebolt 41 when the latter assumes the angular position shown in FIGS. 1 or 4.

The operation is as follows:

When the'user applies pressure against the actuatingmember 6, the shaft 7 of the prime mover rotates thegear 8 whereby the roller 9a orbits about the axis of theshaft 10 and moves thecarriage 11 andcylinder 13 back and forth with reference to the barrel of the housing 1. Thearm 14 shares at least some axial movements of thecylinder 13 whereby the cushions of air in thechambers 15, 16 prevent thepiston 14a from striking thecylinder 13 andcarriage 11 with an excessive force. The steeply inclinedthreads 19, 20 cause the sleeve 21 to turn back and forth about theaxis 24. For example, the sleeve 21 can turn in a clockwise direction when thecylinder 13 performs a forward stroke in a direction toward thefront portion 39 of the housing 1. Thesplines 25 cause theclutch element 26 to rotate withrthe sleeve 21 and theflanks 28a ofteeth 28 on theclutch element 26 rotate theteeth 29 of theclutch element 30 when theclutch element 26 turns in a clockwise direction. When theclutch element 28 turns in a counterclockwise direction, theinclined flanks 28b ofteeth 28 slide along theteeth 29 of theclutch element 30 against the opposition ofclutch spring 27. Thus, and if theshank 45 of thetool 43 shown in FIG. 5 is inserted into thebore 46 of theholder 33, thetool 43 is rotated stepwise in a clockwise direction but does not rotate in a counterclockwise. Theholder 33 receives torque from the internal splines of thesocket 23 which rotates with theclutch element 30.

Whether or not the 43 receives axial impulses from theram 14 depends on the axial position of theanvil 34 with reference to thestem 14b of the ram when the latter approaches the end of or completes a forward stroke toward theend portion 39. Theholder 33 can be moved axially toward thecylinder 13 in response to pressure transmitted thereto by thetool 43, i.e., the tip of the tool can be pressed against a workpiece with a force which suicies to overcome the resistance of thespring 37 and to shift theholder 33 and itsanvil 34 toward theram 14. When theholder 33 assumes the foremost axial position shown in FIG. 1, the stroke of theram 14 is too short so that thestem 14b cannot strike against theanvil 34. The force of blows transmitted by theram 14 depends on the extent to which thespring 37 is compressed, i.e., on the extent of axial displacement of theflange 35 away from thestop surface 38 of thefront end portion 39.

If thetool 43 meets an excessive resistance to rotation in the clockwise direction, theclutch element 26 begins to turn with reference to theclutch element 30 when the sleeve 21 turns in either direction. This is made possible by the slight inclination of tooth anks 28a with reference to the axis 24 (see FIG. 3). Thus, the clutch 4 is a safety clutch which is disengaged in automatic response to excessive resistance offered byholder 33 to rotation of theclutch element 30. This feature insures that the parts of the apparatus are protected against damage and prevents injury to the operator or to persons standing nearby.

When the user replaces thetool 43 with thetool 43A of FIG. 6, theshank 47 cannot be rotated by theholder 33 but the user can drive the tip of thetool 43A into wood or other material if theholder 33 is moved axially rearwardly against the opposition ofspring 37 to place itsanvil 34 into the range of thestem 14b. The hexagonalmedian portion 48 of thetool 43A is then non-rotatably received in thebore 40 of thefront end portion 39.

Theram 14 preferably strikes theanvil 34 upon completed rotation of theholder 33, i.e., when thecylinder 13 reaches the forward end of its stroke and the ram travels forwardly due Ito inertia and against the opposition of air cushion in thechamber 15.

An important advantage of my power tool is that reciprocatory movements of the driver assembly 3 are converted into rotary movements of theclutch elements 26, 30 in a very simple and space-saving manner. Furthermore, one component (ram 14) of the driver assembly 3 also serves as a means for transmitting impacts to theholder 33 for thetool 43, 43A or another tool. The force of such impacts can be regulated by the user in a very simple way and excessively resistance offered by thetool 43 to rotation results in automatic disengagement of the clutch 4 to prevent damage or injury. The parts of my power tool can be made suliciently rugged to withstand extensive and repeated use, and the bias of theclutch spring 27 can be adjusted (or this spring can be replaced by a different spring) if the user wishes to select a different resistance which leads to disengagement of the clutch 4. Similar results can be achieved by replacing theclutch elements 26, 30 with clutch elements whereon the inclination offlanks 28a and/or 28b is different from that shown in FIG. 3.

Thespring 27 is stressed sufficiently to prevent rebounding ofclutch element 26 during rotation in a colckwise direction so that this element can drive theclutch element 30 andholder 33 as long as thecylinder 13 moves forwardly.

Without further analysis, the foregoing will so fully reveal the gist of the present invention .that others can, by applying current knowledge, readily adapt it for various applications without omitting features which fairly constitute essential characteristics of the generic and specific aspects of my contribution to the art.

What is claimed as new and desired to be protected by Letters Patent is set forth in the appended claims:

1. In a power tool for rotating and/or transmitting axially oriented impacts to drilling, boring, chiseling or like tools, a combination comprising a housing; a driver assembly mounted in and reciprocable axially of said housing; a tubular member rotatably mounted in said housing; coupling means provided on said tubular member and on said driver assembly to turn the tubular mem- -ber back and forth in response to reciprocation of said assembly; disengageable clutch means including a first element connected for rotation with said tubular member, a second element rotatable in said housing, and biasing means for urging one of said elements axially against the other element, said elements having complementary teeth arranged to transmit torque from said rst to said second element in at least one direction and to move apart against the opposition of said biasing means when the resistance offered by said second element to rotation with said first element in said one direction exceeds a given value; and an axially movable tool holder connected for rotation with said second element and having an impact receiving portion movable into the range of said driver assembly.

2. A combination as defined in claim 1, wherein said coupling means comprises steep threads provided on said driver assembly and complementary steep threads provided on said tubular member.

3. A combination as defined in claim 1, wherein the teeth of said elements of said clutch means resemble saw teeth.

4. A combination as defined in claim 1, wherein said second element of said clutch means comprises a socket axially movably accommodating said impact receiving portion of said tool holder.

5. A combination as defined in claim 1, wherein said driver assembly comprises a cylinder movable axially in said housing and a ram movable axially with and relative to said cylinder.

6. A combination as defined in claim 5, wherein said ram comprises a portion dividing the interior of said cylinder into a pair of air-filled chambers wherein the air opposes axial movements of said ram relative to :said cylinder.

7. A combination as defined inclaim 6, wherein said Iam comprises a second portion extending from said cylinder and arranged to strike against said impact receiving portion when said tool holder is moved axially toward and sufiiciently close to said driver assembly.

8. A combination as defined inclaim 6, wherein said cylinder has at least one air flow restricting opening connecting said chambers with the atmosphere.

9. A combination as defined in claim 5, wherein said cylinder has a smaller-diameter front portion adjacent to said clutch means and surrounded by said tubular member, said coupling means comprising steep external threads provided on said front portion and steep internal threads provided on said tubular member and meshing with said external threads.

10. A combination as defined in claim 1, wherein said tubular member is formed with axially extending splines receiving projections provided on said first element of said clutch means so that said first element is movable axially of said tubular member.

11. A combination as defined inclaim 10, wherein said biasing means comprises resilient means operating between said tubular member and said rst element to urge the latter axially toward and against said second element of said clutch means.

12. A combination as defined in claim 1, further comprising a socket rigid with said second element of said clutch means and axially movably accommodating a portion of said tool holder.

13. A combination as defined in claim 1, wherein the teeth of said elements of said clutch means have flanks making an acute angle with the axis of said housing.

14. A combination as defined in claim 1, further comprising second lbiasing means for urging said tool holder away from said tubular member to normally maintain said impact receiving portion outside of the range of said driver assembly.

15. A combination as defined inclaim 14, wherein said housing comprises stop means and said tool holder nor. mally abuts against said stop means under the action of said second biasing means.

16. A combination as defined in claim 1, further comprising retaining means provided on said housing adjacent to said tool holder and movable into retaining engagement with a tool which is inserted into said holder.

17. A combination as defined inclaim 16, wherein said retaining means comprises a bolt turnable in elastic bearings provided therefor in said housing.

18. A combination as defined in claim 1, wherein said driver assembly comprises a carriage reciprocable in ways provided therefor in said housing and having a transversely extending slot, and further comprising means 8 for reciprocating said carriage including a driven member rotatable about a second axis which is substantially normal to the axis of said housing and having an eccentric portion extending into said slot.

19. A combination as defined inclaim 18, wherein driven member forms part of a transmission and further comprising a prime mover having an output portion mounted in said housing and operatively connected with said transmission.

20. A combination as defined in claim 1, wherein said one element is said first element of said clutch means and said biasing means comprises a helical spring operating between said first element and an external projection of said tubular member.

References Cited UNITED STATES PATENTS 2,700,373 1/1955 Feucht 173-111 3,029,672 4/1962 Lwenborg 173-111 3,275,088 9/1966 Schrttle 173--110 JAMES A. LEPPINK, Primary Examiner U.S. Cl. X.R.

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