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Publication numberUS2861778 A
Publication typeGrant
Publication dateNov 25, 1958
Filing dateOct 7, 1954
Priority dateOct 7, 1954
Publication numberUS 2861778 A, US 2861778A, US-A-2861778, US2861778 A, US2861778A
InventorsSpurlin William V
Original AssigneeSyntron Co
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Electromagnetic reciprocating hammer
US 2861778 A
Abstract  available in
Images(1)
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Claims  available in
Description  (OCR text may contain errors)

Nov. 25, 1958 W. V. SPURLIN ELECTROMAGNETIC RECIPROQATING HAMMER Filed Oct JNVENTOR.

W/L /AM M Spam, fu

" nited States ELECTROMAGNETHI RECIPROCATING HAMMER William V. Spurlin, Indiana, Pa., assigner to Syntron Company, Homer'City, Pa., a/corporation-y of Delaware Application October 7, 1954,(Serial No. 450,822

4 Claims. (Cl. Z55-37) and heavy being made for mounting on a mining machiner or similar apparatus for having its tool operate independently. The free magnetic piston or core in this hammer reciprocates to follow the fields of alternate coils energized by intermittent current impulses and moves throughV a stroke of one inch at the rate of 1,800 cycles per minute delivering a striking force of 30,000 pounds, measured by means of a strain gauge, with the hammer mounted onv a special test stand.

This force in a free body requires guided distribution of the forces expended within the hammer during its reciprocation. A principal object of this invention is the provision of an impact plate to receive the spring biased force of a core stop after being disengaged by the core.

This impact plate relieves the core bearing assembly of" this force.

Another object of this invention is the provision of stepped ends between the stems and the body of the core. These stepped ends being smaller in diameter than the body and larger than the stems are not as effective on the magnetic ilux, yet they provide the needed strength at this great change in radii from the body to the stems.

Another object of this invention is the provision of reduced clearance to limit the travel of the tool stop seat and prevent continuous flexing of the spring disk between the tool bushing assembly and the tool stop seat. This spring'disk maintains pressure on these parts keeping them in contact with each other. the tool by its spring acting through the tool stop exerts pressure on the ange of the tool until the tool stop engages the tool stop seat at which time the spring'force` acts to compress the disk through only a limited extent ing of the spring disk which still maintains pressure beas the shoulder in the nose casting prevents further extween the tool bushing assembly and the tool` stop seat.

This limited exing of the spring disk permits theV latter to accomplish its purpose and at the same time avoids excessive flexing which breaks ther spring disk due to fatigue.

Other objects and advantages of this invention appear hereinafter in the following description and claims.

The accompanying drawing shows for the purpose of exemplification without limiting the invention or claims thereto, certain practical embodiments vof the invention wherein the single view is in horizontal section ofthe electric hammer. f Referring to the drawing, Vthe electric hammer is constructed on the stainless steel barrelflgwhichfhas avcylinr' drical bore 2 that forms the magnetic, piston -chamberf3.,

The exterior of the barrel 1 has hexagonal faces that are The return stroke of' atent ICC dual sections11 are connected with a heavy center plate- 12 which stops short of the barrel as shown at 13 and does not extend to the outer surface as indicated; Each L-shaped lamination 10is connected to one of the dualsections 11v by a straight outer lamination member 14 to close the outer magnetic circuit over the coils 1S and V16.

This avoids excessivefmagnetic'losses in the outer steelcylindrical casing 17.

Each of the six sets of laminations 10 and 11 are welded along only one side and at theirends'to the exterior of the barrel, as indicated at 18. This breaks the path of the eddy currents by having the laminations welded only on one side andA at fthe ends.

Each circular set of the laminations 10 and 11 has high temperature insulating cord 20 Awound between the insulating ends 21 to fill uptheinterlocking notches in thelaminations 'as the-magnetic gap 22 and thus provide abase for the coil. Each coil is wound ofsquare'wire which aids in locking'the coil in place where wire of circular cross section may shift. `Again av numberof circular mils` may be obtained fora given length and num-.- The coilI leads '23 are brought out between the coils and yare providedf with expansion loops' ber of` turns of wire;

24, to avoid' destruction ofthe coil due to expansion and contraction dueto heatgas-these coils are not ventilated' but are completelyenclosed. l

The end castingsZS and26 are mounted to engage the cylindrical end'sy 7T andS of the barrelfl which seat on* shoulders in'V these end castings and preventv these end castings from engaging the coil "laminations 'TheseV endcastings are madefof manganese'bronze and each is provided with a cylindrical seat Z7' of material width whichy terminates inthe sharp groove 28. The ends ofthe casing 17 have a beveled sharp edge that'ts in to the sharp grooves 28 and their Vinner surfaces are machined to tightly lit on the seats 27 to provide a gastight seal ofthe coil chamber '30 within the case 17.

Tie rods, not shown, are bolted to the front end casting 2S andthe'rear end casting 26. These tie rods cause the ends of the casing 17' to bite into the V-shaped grooves 28 of the end castings and hold the latter castings in assembled relation with the barrelv ll andthe outer cas,- ing 17.

The Vcylindrical bore of the barrel 1 has the shoulders..

3 4 and 35 for receiving the complemental shoulders on the bearings 36 and 37 which arer'accurately formed and positioned Ato provide aligned bores in whichgto receive.

the stems 3.8 of the free electromagnetic piston 40., yThe piston 40 must Lbe of magnetic material, lt must be intcgral, made of one piece, audit must be strong.` It is therefore constructed as a, forging. Between the body of the core, the stems 33 and the piston 40 an. annular` step 39 is formed. The annular step is lletedto the.

small diameter of the stems and is also iillcted to the large diameter of the central body of the core. ,These stepped and ll'eted reenforcements of this forging materiallystrengthen the piston where a great reduction in diameteris'required. However, these stepped fillets doi not alter the operationoffthis magnetic core. It isp'refer-l able to polish these fillets as well as the other faces of thiscore. This maintains asirro'oth surface that is not apt to fracture due to the high impact loads it must transmit.

The ends of the piston stems 38 have the contact surfaces capped with stellite by welding the same thereto, as indicated at 41.

The body of the piston 40 is tinted longitudinally by eight slots 42 which are cut approximately one quarter of an inch deep. These slots serve two purposes of equal importance. One, they reduce the eddy currents by interrupting their paths of ow. Secondly, they provide channels through which the atmospherein the piston chamber 3 may be quickly forced vfrom one end of the chamber' to the other and avoid the generation of excessive pressure and rarefication zones.

The bearings 36 and 37 provide for only a few thousandths of an inch for sliding clearance between the stems and bores of these bearings. Each bearing has an annular external groove 43 which has an annular wick 44 and radial wicks 45 which conducts the oil to the surface of the stems. These oil reservoirs 43 are lubricated through passages that extend from the bearings 36 and 37 into the end castings 25 and 26 where they extend to the surface and are provided with ball check oil seal iittings.

The front end casting has the tool bushing assembly mounted in its inner end and which comprises the housing 46 which is bored from its inner end to receive the tool bushing 47 that slidably supports the tool shank 48 that is lubricated from the passage 49.

The shoulder 50 of the tool is approximately threefourths of an inch thick and the fillets to the tool shank 48 and the tool bits 51 are three-eighths of an inch. The shank 48 is ground to one and one-halt:` inches, whereas the tool 51 is ground to 1.875 inches for a distance of thirteen inches from the shoulder edge. This is larger than the shank and extends to the end of the nose casting 52. The tool is thirty inches over-all, the shank is six inches, thus the balance of the bit is approximately ten and one-quarter of an inch long and this length tapers from 1.875 inches to 1.5 inches and the end of the bitlis a flat transverse face 53. These dimensions are important owing to the manner that the tool is supported.

The end casting 25 extends forwardly and has an internal shoulder 54 to receive the inner end of the nose casting which is bolted thereto by the bolts 55 which also bolt on the roof trimming blade 56 Which has a sharpened tooth to chip the roof smooth as the whole hammer is reciprocated. The nose casting 52 is bored to receive the bearing 57 which rests on the shoulder 58, leaving space for the circular ring packing 60. Another ring packing 61 is mounted in a groove adjacent the other end of the bearing 57. Thus the bearings 47 and 57 suspend the tool and one is mounted in the housing 46 and the other in the nose casting 52, both of which are aligned in coaxial bores in the end casting 25. Lubricating passageway 62 is provided to lubricate the tool bit 51 through the nose casting between the ring seals.

A lock sleeve 63 is a tool stop seat placed in the bore of the end casting 25 and abuts the nose casting 52 at one end but is spaced from the housing 46 at its other end. This space provides room for the continuous circular spring washer 64. The clearance 59 between the end of the end casting 25 and the lock sleeve or tool stop seat 63 is materially less than the clearance between the lock sleeve 63 and the bearing housing 46 where the circular spring washer is seated. The reason for this is to prevent the spring 66 from collapsing the washer 64 at each stroke of the piston causing fatigue of the spring washer. Thus by reducing the clearance 59 the spring washer 64 is flexed very little and it continues to maintain its pressure between these parts.

The interior of the nose casting has a seat 65 to receive one end of the coil spring 66, the other end of which engages the spring seat 67. This spring seat 67 has clearance with the tool bit 51 and the bore of the lock sleeve 63.

A bell opening is provided in the bores of the housing 46 and the spring seat 67 to receive the tilleted sides ofthe tool shoulder 50 which engages both of these parts, the rst as a rebound from the coil or due to the spring and secondly at the end of the power stroke when the piston stem 38 engages the shank 48 of the tool.

The end casting 26 has the rear spring support 70 :bolted thereto by the bolts 71. The support 70 is open and has an end cap 72 which seats the outer end of the spring 73 and is secured by the bolts 68. The springs 66 and 73 are the same in size and shape. The other end of the spring 73 engages the solid core stop 74 which has a projection 75 that reciprocates in the bore of the core stop guide 76 which is retained by the heavy plate 77 bolted between the end casting 26 and the spring support or head casting 70. The core stop 74 engages the impact plate 77 when the stern of the core leaves the stop 74. The force of the core stop striking the impact plate 77 is due to the spring 73. None of these forces are transmitted axially to the bearing 37 or the core stop guide 76.

When the coils 15 and 16 are energized by alternate electric impulses the core piston 40 reciprocates toward the center of one coil then the center of the other coil causing the capped ends to Strike the projection 75 of the core stop 74 compressing the spring 'i3 and then traveling in the opposite direction to strike the shank 48 of the tool bit 51 which moves the toolagainst the work being performed in the ground until the flange 50 strikes the spring seat 67 to compress the spring 66. As the piston 40 returns the spring 66 acts through the spring seat 67 to force the tool stop seat 63 to strike the nose casting 25. The bearing housing is thus relieved from this return blow of the spring 66. The sarne is true of the opposite end of the hammer where the heavy impact plate 77 and the casting 26 takes the blow of the spring 73 through the core stop 74 and the bearing assembly 37 is relieved of this shock.

l claim:

l. An electromagnetic reciprocating hammer comprising a tubular housing having spaced coaxially mounted coils, a nose casting on one end and a head casting on the other end of said housing, a magnetic core reciprocally mounted in said housing and operated by said coils, said core having a body portion with a stem at each end, bearings carried by said housing to slidably support said stems, said nose casting carries a tool with a ange and having a bit end and a shank end on opposite sides of the flange, a tool stop engaging said tool ilange, spring means in said nose casting urging said tool stop against the ange of said tool, a tool stop seat slidable with limited clearance in said nose casting and engaged by said tool stop, a tool shank bushing, and a spring disc between the tool stop seat and the bushing capable of greater flexible movement when in place than the tool Vstop seat clearance will allow.

2. An electromagnetic reciprocating hammer having a tubular barrel carrying bearings and nose and head castings at opposite ends with spaced coaxially mounted coils mounted between said castings, a magnetic core having a body portion with axially projecting stems slidably supported in said bearings to reciprocally support said body portion in the barrel under the eifect of the magnetic eld produced by the alternate energization of said coils, characterizedin that the body and stems of said core are made from a single integral piece of magnetic material, and an annular step of reduced diameter formed between the body and each stem to make the magnetic flux less effective on the core ends.

3. The electromagnetic reciprocating hammer of claim 2 characterized in that each of said steps has a llet to the small diameter of each stem and a llet tothe large diameter of said body portion.

4. An electromagnetic reciprocating hammer comprising a tubular housing-having spaced coaxially mounted coils, a nose casting on one end and a head casting on the lother end of said housing, a magnetic core reciprocally mounted in said housing and operated by said coils, said core having a body portion with a stem at each end, bearings carried by said housing to slidably support said stems, a retaining impact plate mounted transversely between said head casting and said housing and having a transverse opening aligned with the core stem, a core stop seated on the outer face of said plate, a projection on said core stop extending through said plate opening References Cited in the le of this patent into said bearing in the path of said core stem, and 10 1,753,454

spring means urging said core stop against said plate.

UNITED STATES PATENTS Wagner Apr. 18, 1905 Grose May 8, 1907 Weyandt Aug. 14, 1928 Donaldson Nov. 6, 1928 Weyandt Mar. 12, 1929 Weyandt Apr. 8, 1930

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US787707 *Dec 7, 1904Apr 18, 1905American Inv S CompanyElectric tool-driver.
US937237 *May 8, 1907Oct 19, 1909James Edward Hoskins GroseRock-drilling machine.
US1680311 *Feb 1, 1926Aug 14, 1928Central Electric Tool CompanyReciprocating motor
US1690571 *Nov 24, 1923Nov 6, 1928Shearman Donaldson JohnTool and tool retainer
US1705079 *May 5, 1926Mar 12, 1929Central Electric Tool CompanyReciprocating motor
US1753454 *Mar 30, 1925Apr 8, 1930Central Electric Tool CompanyElectric percussive tool
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3387671 *Oct 15, 1965Jun 11, 1968Mission Mfg CoPercussion tool
US3411591 *Mar 3, 1966Nov 19, 1968Hughes Tool CoCoil power spring impact mechanism
US3460637 *Aug 21, 1967Aug 12, 1969Wacker Werke KgOscillating working device
US3995703 *May 5, 1975Dec 7, 1976Robert Bosch G.M.B.H.Electrohydraulically operated portable power tool
US4015671 *Apr 17, 1973Apr 5, 1977Vladimir Mikhailovich BorisovElectric hammer
US4353426 *Aug 15, 1980Oct 12, 1982Dobson Park Industries LimitedPercussive tools
US4548278 *Jan 23, 1984Oct 22, 1985Atlas Copco AktiebolagPercussion tool
US4831292 *May 27, 1988May 16, 1989Hughes Aircraft CompanyLinear motor arrangement with center of mass balancing
US6224009 *Jul 6, 1999May 1, 2001L.G.L. Electronics S.P.A.Device for modulated braking of a weft yarn for textile machines
US6695070 *Aug 5, 2002Feb 24, 2004Matsushita Electric Works, Ltd.Magnetic impact device and method for magnetically generating impact motion
US7503400 *Jan 30, 2004Mar 17, 2009Arrow Fastener Co., Inc.Two shot power nailer
US8225978 *Aug 6, 2009Jul 24, 2012Black & Decker Inc.Multistage solenoid fastening tool with decreased energy consumption and increased driving force
US8353435 *Jul 20, 2012Jan 15, 2013Black & Decker Inc.Multistage solenoid fastening tool with decreased energy consumption and increased driving force
CN100486778CJul 13, 2006May 13, 2009陈一定Electromagnetically vibrating impactor
Classifications
U.S. Classification173/117, 310/30, 310/23, 173/202
International ClassificationE21B1/22, B25D11/06, B25D13/00, E21B1/00, B25D11/00
Cooperative ClassificationB25D11/064
European ClassificationB25D11/06E