US792591A - Metal-working machine. - Google Patents
Metal-working machine. Download PDFInfo
- Publication number
- US792591A US792591A US16706803A US1903167068A US792591A US 792591 A US792591 A US 792591A US 16706803 A US16706803 A US 16706803A US 1903167068 A US1903167068 A US 1903167068A US 792591 A US792591 A US 792591A
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- United States
- Prior art keywords
- shaft
- gear
- head
- spindle
- gears
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23B—TURNING; BORING
- B23B7/00—Automatic or semi-automatic turning-machines with a single working-spindle, e.g. controlled by cams; Equipment therefor; Features common to automatic and semi-automatic turning-machines with one or more working-spindles
- B23B7/12—Automatic or semi-automatic machines for turning of workpieces
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
- B23Q1/01—Frames, beds, pillars or like members; Arrangement of ways
- B23Q1/015—Frames, beds, pillars
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/51—Plural diverse manufacturing apparatus including means for metal shaping or assembling
- Y10T29/5152—Plural diverse manufacturing apparatus including means for metal shaping or assembling with turret mechanism
- Y10T29/5154—Plural diverse manufacturing apparatus including means for metal shaping or assembling with turret mechanism tool turret
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T82/00—Turning
- Y10T82/25—Lathe
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T82/00—Turning
- Y10T82/25—Lathe
- Y10T82/2552—Headstock
Definitions
- This invention has relation to metal-working machinery, and while it is more particularly applicable to that class of machines in which the work is rotated relatively to the tool, yet it is well adapted for other classes of metal-working machinery.
- the object of the invention is to provide, first, a head having power-transmitting mechanism for effecting a differential rotation of the spindle from a constantly-rotated powershaft, with controlling means whereby the speed of rotation of the spindle may be graded from a relatively low speed to a relatively.
- Figure 1 represents in side elevation the head end of a metal-working lathe, preferably of the type in which a turret carries the tools to operate upon the work.
- shaft 122 is broken off and pulley 123 is omit-ted.
- Fig. 1 shows in side elevation a lathe enibodying the invention.
- Fig. 1" represents a plan view of the same.
- Fig. 2 represents an end elevation, of the head of the machine.
- Fig. 3 represents a partial section transversely through the bed from front to rear.
- Fig. 10 represents a partial section through the machine from front to rear and represents the mechanism for controlling the worm by which power is imparted to the feed-screw for the head.
- Fig. 11 represents a front elevation of the gearing shown in Fig. 9.
- Figs. 12 and 13 illustrate the movable double worm for the feed-screw for the head.
- Fig. 14 represents in plan view the head end of the machine, with the top of the head removed to show the power-transmitting mechanism contained therein.
- Fig. 15 represents a section through the head end of the machine.
- Fig. 16 represents a horizontal section through the head in a plane coincident with the axis of the spindle.
- Fig. 17 represents an enlarged longitudinal section of the controller for one of the friction-clutches, which may be termed the reversing-gears in the head.
- Fig. 18 represents an enlarged section on the same plane as that on which Fig. 16 is taken and illustrates the single controller for the differential ratchet mechanism.
- Figs. 19 and 20 illustrate the controller in different positions.
- FIG. 21 represents a view of the controller detached and looking at its under side or face.
- Figs. 22 and 23 illustrate the operation of the controller.
- Fig. 24 represents a perspective view of the end of the powershaft.
- Fig. 25 represents the member in said shaft which controls the clutch-pin.
- Fig. 26 represents the end of the shaft and the rod or member in their operative relation.
- Fig. 27 is a section on the line 27 27 of Fig. 16.
- Fig. 28 represents a similar section through two of the gears or ratchet-clutches.
- Fig. 29 represents one of the ratchet-clutches in perspective view.
- Fig. 30 represents a section through one of said clutches.
- 'Figs. 31 and 32 represent the two members of one of the ratchet-clutches.
- Figs. 33 and 34 represent the ratchet-clutch on the back gear.
- Fig. 35 represents a section on the line 35 35 of Fig.
- Fig. 36 represents a section on the line 36 36 of Fig. 14.
- the present invention may be embodied in a turret-lathe such as set forth in Letters Patent No. 15 7,967, granted to me August 18, 1891, in which there is a carriage 10, movable longitudinally on the bed, a feedrod 70 for effecting the movement of the carriage, a turret 4L1 on the carriage, automatic stops (not illustrated) for the carriage, and other features forming a part of the lathe.
- T/m fim/(L 'fhe lathe-bed is indicated at and has the usual ways or shears 12 for the turret-carriage.
- At the head end it is provided with forwardly and rearwardly extending portions 51 52, which are provided with parallel ways, guides, or shears 54: at a right angle to the ways for the turret-carriage.
- These guides or shears extend from front to rear transversely of the bed to receive a movable head which contains the spindle and the power-transmitting mechanism therefor.
- Said head comprises a panshaped casing and a top or cover
- This pan-shaped head is relatively shallow and is adapted for the reception of a quantity of lubricant in which the lower portions of the inclosed bearings and trains of gearing may be immersed to insure a thorough lubrication thereof when in operation.
- the top or cover prevents the escape of the lubricant and is readily removed to admit of a conveni ent inspection of the gearing while running and the adjustment and repair of the parts when at rest.
- the casing 55 is provided at its bottom with gibs 58 for taking under the ways or shears 53 54, some of the gibs being provided with adjusting-screws .(Zm0)'/i// n/ecluii/nz'sni.
- the head is provided with a downwardly-projecting portion which forms a nut 60 (see Figs. 3 and 4) for operative engagement with the threads of a feed-screw 61, arranged transversely of the bed between the guides or shears.
- This feedscrew as shown in Fig. at, is journaled at one end in a bracket 62 on the bed and at its other end in a bracket 63, projecting forwardly and upwardly from the front of the bed.
- the forwardly-projecting end of the feed-screw is equipped with a wheel 64, having handles or spokes by which it may be rotated manually to feed the head transversely of the bed in a horizontal direction.
- worm-wheel 65 fast upon the feed-screw 61, a double worm 66 on an inclined shaft 67, having a spiral gear 68 intermeshing with and driven by a complemental gear 69 on a shaft 70, arranged longitudinally of the machine and journaled in a bearing 71 on the front of the bed 52, near the lower end thereof.
- This shaft 70 is utilized as the feed-shaft for the tool-carriage and extends along the bed, as shown in Fig. 1 and as described in Patent No. 457,967.
- the double worm (shown in Figs. 9 to 13, inclusive) it will be observed that it is keyed upon the shaft 67 so as to slide thereon, its ends being held between the arms of a yoke 72. livoted to the yoke there is a latch 73, having notches 74L 75, adapted to be engaged with one of the upright walls forming the inner end of the extension 51, which is slotted for this purpose. This wall for convenience is numbered 76. By lifting the latch, which is provided with a handle 77 for this purpose, the yoke 72 may be moved longitudinally of the shaft 67 to engage either end of the double worm with the worm-wlmel 65.
- the threads on the opposite ends of the worm are relatively rightand left, so that the worm may be shifted to one position or the other in order to feed the head either forward or backward, as desired.
- the lower end of the shaft 67 is rotatively mounted in a knob 78, journaled on the bearing 71, so that the shaft 67 is adapted to oscillate about the axis of the knob to permit the worm to be moved into and out of engagement with the wormwheel.
- a stud-shaft 79 Journaled in the :front of the extension 51 of the bed is a stud-shaft 79, having ahandle 80.
- This stud-shaft is provided with an cecentric 81, so that when the shaft is rocked the yoke, which rests upon the eccentric, may be moved toward and from the feed-screw (51 and the worm-wheel thereon.
- Thehandle 80 of the shaft 79 which serves to raise and lower the yoke and the double worm, and the handle 77 of the latch 73 are exposed in the front of the lathe, so that they may be easily manipulated by the operator, as shown in Fig. 3.
- each of the stop-bars 82 is provided with a recess 88 in its top edge or surface, the walls 89 90 of said recess being beveled to constitute a stop for coaction with a stop on the head.
- These several stop-bars may be adjusted longitudinally, and there are as many of them as maybe desired, six being illustrated in different relative positions.
- the stop on the head consists of a double pawl 91, arranged yieldingly upon a shaft 92, journaled in the end walls of the head, so as to extend in lines parallel to the spindle.
- This shaft 92 is provided with a handle 93, (see Figs. 3 and 5,) and it is adapted to be movedlongitudinally of its axis and transversely of the stop-bars 82.
- the bottom wall of the head is socketed for the reception of the pawl, which is pinned to the shaft 92 by a pin 94. (See Fig. 8.) This pin bears against a spring 95, held in place in the end of the pawl by a screw 96.
- the diametrically opposite pin 97 is seated against the tension of a spring 98 in a socket in the pawl.
- the aperture 99 in the pawl, through which the shaft 92 passes, is in the form of an elongated slot, so as to permit a limited movement of the pawl transversely of the said shaft against the tension of the spring 95 or spring 98.
- the walls of the recess 100 in the bottom wall of the head are such that when the pawl is rocked to the position shown in Figs. 7 and S, for instance, or to that shown in Fig. 6 they form an abutment for the non-acting end of the pawl.
- the shaft 92 is located above the stop-bars 82, so that by rocking it either end of the pawl may be caused to drop into one of the notches in the stop-bar, this being accomplished manually in the illustrated embodiment of the invention.
- the feed-shaft is frictionally driven, as will be explained, so that as soon as the pawl engages one of the inclined walls (or shoulders, as they may be termed) 89 90 on one of the stop-bars the head will be positively held against movement as soon as the inactive end of the pawl comes into engagement with one of the walls in the recess 100, or the operator may by oscillating the handle drop the double worm to an inactive position as soon as he observes that the pawl has engaged the shoulder upon the stop-bar.
- the shaft 92 By moving the shaft 92 longitudinally the double pawl may be brought into the vertical plane of any one of the six stop-bars. Consequently the operation may effect the stopping of the head in either direction in any predetermined position thatmay be desired.
- any convenient form of multiple stop may be used in lieu of that shown.
- the work may be shifted with relation to the turning or other tool which is operating upon the work.
- This is of advantage in many kinds of work and obviates the necessity of mounting a cross-slide upon the turret to the exclusion of other tools which it may be desired to use, since such cross-slides require a considerable amount of space upon the turret.
- the movable head likewise enables the work to be fed against a cutting-off tool or against a general shaping or face tool when their use is necessary, and which may be mounted stationarily upon the turret or upon some part of the bed.
- -Tl16 feed-shaft 70 from which power is transmitted to the feed-screw for the head, is driven frictionally, being providedwith oppositely-beveled friction-disks 101 102, which are engaged with complemental driving-disks 103 104:, mounted upon a shaft 105, journaled in a yoke 106.
- This yoke is in turn journaled upon a shaft 182, which projects from the head, as will be explained.
- the shaft 182 is equipped with a spiral gear 107, intermeshing with and driving a complemental gear 108 on a shaft 109, journaled in bearings on the yoke 106, as illustrated in Fig. 2.
- the said shaft 109 carries at its lower end a spiral gear 110, intermeshing with and driving a complemental gear 111 on the shaft 105.
- the yoke 106 may be swung about its fulcrum to move the driving friction-wheels 103 10 1 toward the axis of the shaft or away therefrom to cause engagement or disengagement of the disks 103 10 1 and disks 101 102.
- a cam 113 arranged in the rear of the yoke, a cam 113, engaging with a complemental cam 11% on the lower end of the yoke 106.
- a lever 115 Secured to the earn 113 or to the shaft 112 there is a lever 115, by which the shaft may be rocked and the cam oscillated to move the yoke 106, as will be readily understood.
- the arm or lever 113 will remain in whatever position to which it is adjusted.
- This mechanism provides a convenient means for frictionally driving the feed-shaft for the toolcarriage and the screw-shaft for the head.
- the main driving-shaft is indicated at 122, and it projects at its end beyond the head for the reception of a belt-wheel 123, by which it may be rotated in one direction and at a constant speed.
- This shaft is journaled in boxes 124 124:, which are driven into the supports 120 121, and it is held against longitudinal movement by collars 125, rigidly secured thereto and bearing against said boxes.
- Each box tapers outwardly and is formed with ashoulder to bear against theinner face of the web or support 120 121, as the case may be.
- the spindle is indicated at 126. It consists of a hollow shaft having a smooth unshouldered periphery or exterior surface. In this respect it is essentially different from any of the spindles which have been heretofore used in metal-working machines. On its inner end it is equipped with a chuck 127.
- the spindle is held against movement by the following devices: Secured to the spindle by two screw-pins 128 128 is the common hub of two gears 129 and 180.
- a flange or web 131 On one side of the gear 129 is a flange or web 131, which is cast with the casing or head, and between the said liange and the end of the hub of the wheel are two loose washers 132 133.
- On the opposite side of the gear 130 are two similar loose washers 13 1 and 135, and bearing upon the washer 135 are two set-screws 136 136, passed through ears or lugs 137, east integrally with the head.
- the gears 129 130 may be clamped against axial movement and by reason of their pinned connection with the spindle hold said spindle against movement longitudinally of its axis.
- the spindle may be removed as an entirety from the head by drawing upon the chuck end of it.
- the spindle is mounted in boxes 138 138, which are exteriorly tapered and are set in the supports 120 121 in tapering apertures provided for their reception. Between the boxes and the shaft are placed bushings 139 110.
- each box or bearing is formed with a cavity 112 for the reception of lubricant and also for the reception of a loose ring 1413, which assists in carrying the lubricant to the'various parts of the bearing.
- the speed variation is effected by clutch mechanisms, the finer gradations of speed being secured by positive ratchet-clutches with devices which insure their operation in proper sequence and the greater or coarser gradations being secured by main clutches.
- the entire range of the liner gradations in speed or the difference between the lowest speed and the highest speed secured by the ratchet-clutches is about equal to the range or difference in speed secured by the main clutches.
- the lov-speed main clutch may be operated while the ratchet-clutches are operated from relatively low speed to relatively high speed, and then by throwing in the high-speed main clutch the ratchet-clutches may be again operated in sequence from relatively low to relatively high, with the result that the munber of fine gradations in speed are equal to the number of ratchet-clutches multiplied by the number of main clutches.
- back gearing inclnding a back-gear clutch which can be operated coincidently with the ratchet-clutches for securing gradations of speed still lower than those secured by the use of the main clutches.
- the spindle is provided with gears 129 130, as previously described, to which power is imparted by trains of gearing, as will be explained, for the purpose of driving the spindle in one direction or the other, these trains of gearing being interposed between the power-shaft 122 and the spindle.
- the 1 )ower-shaft and the spindle four shafts, which may be termed the secondary power-shaft, the back-gear shaft, an intermediate shaft, and a reverseshaft.
- the power-shaft, the secondary power-shaft, and the intermediate shaft all have their axes located in the same horizontal plane as the spindle, this plane being coincident with the plane of division between the bottom portion of the casing or head and the cover thereof,
- Rafa/mi (ifllfli/l/ wmc/m/iismr Tlle prime power-shaft 122 has pinned to it three gears 14st 1 15 1 16, which intermesb, respectively, with gears 117 M8 149, all loosely mounted upon the secondary power-shaft 150. There are likewise loose upon the power-shaft 122 the following gears 151, 152, and. 153, respectively intermeshing with the gears 154: 155 156, all of which a re pinned to the shaft 150.
- the shaft 150 may be d rivcn at any one of six speeds relatively to the shaft 122, the ratios of the pairs of coacting gears being such that each increase in speed of the shaft 150 is twenty-live per cent. over the preceding speed.
- the gears 14:4, 145, and 1 16 all rotate in unison with the shaft 122, and therefore the gears 1 17, 1&8, and 119 are constantly in rotation loosely upon the shaft 150.
- Additional clutches are interposed between the last-1nentioned three gears andv the shaft 150, and similar clutches are interposed between the loose gears 151 152 153 and the shaft 122, these clutches providing for the liner gradation of speed of the spindle.
- Each of the fast gears on each of the two shafts 122 carries a loose pawl 160, which is adapted to be thrust inward by a spring 1611, as shown in Fig. 30.
- This pawl is placed in a socket formed in a disk-like member carried by the gear and rests loosely upon a pin 161, arranged radially of the gear and passing through an aperture in the shaft.
- the two shafts are hollow for the reception of rotatable members or rods 162 163, against which the ends of the pins 161 bear.
- Each of the loose gears 151, 152, and 153 on the shaft 122 and the gears 147, 148, and 149 on the shaft 50 is keyed to a sleeve or bushing 16 1, loose upon its respective shaft.
- This sleeve or bushing in each case is formed on its end with ratchet-teeth 165 and fits into a socket within the disk-like hub of the next adjacent gear, so that the ratchet-teeth arein a potential relation to the pawl 160, carried by said gear.
- the fast and loose gears are mounted in pairs the fast gear 1 11, for instance, carrying a pawl adapted to engage the ratchet of the gear 151, the gear 1415 carrying a pawl for the ratchet-gear 152, and the gear 146 carrying a pawl for the ratchet of gear 153.
- the arrangement of the gears on the shaft 150 is similar to that just described, there being upon each shaft three pairs of gears having pawls and ratchets arranged in potential relation.
- This pawl -andratchet mechanism forms in each case a positive ratchet-clutch by which the loose gear may be positively keyed to the fastgear.
- the pins 161 control the operation of the various pawls 160, mechanism being provided by which these pins are moved into and out of active or inactive position, as the case may be, said mechanism being such that only one pin is active at a time and the pins are actuated in proper sequence.
- the rotative members or rods 162 163 are held against longitudinal movement by setscrews 166, formed in an extension on theinner end of the casing or head, said set-screws being locked in place by additional set-screws 167, arranged at right angles thereto.
- Each rod 162 or 163 is provided with three recesses or sockets 168, into which the pin 161 may drop when permitted. These sockets are out of line with each other and may be formed by simply flattening the rod 162 163 or forming a short groove in the periphery thereof. The rod may be rotated as in the case of the rod 162, (shown in Fig.
- each rod may be rotated so as to bring a socket 168 under one of the pins 161, as shown in the case of the rod 163 at the left end thereof, where the pin 161, carried by the gear 154:, is shown as dropped into a socket, so as to permit the pawl to engage the teeth of the ratchet of the gear 1 17. Consequently the shaft 150 may by properly rotatively adjusting the rods 162 and 163 be driven at any one of six speeds from the shaft 122.
- a controller is provided for eifecting the relative rotation of these rods and is so constructed that the clutchpins 161 are permitted to drop into active position in a predetermined order, beginning with the coacting gears having the lowest ratio and ending with that pair of gears having the greatest ratio-to wit, those indicated at 153 and 156-whereby the shaft 150 is driven gradually from its lowest to its highest speed, the increment of increase being twenty-five per cent. over the preceding rate of speed.
- the controller for the rods 162 163 is best shown in Figs. 18 to 26, inclusive.
- Each of the rods 162 163 is formed with a finger 170, adapted to be engaged by an abutment 171.
- These two abutments constitute stops hinged to a carrier 172.
- This carrier is secured to an upright shaft 173, journaled in the extension 171 of the head or casing, and is equipped on its end with a handle 175, by which it may be depressed and rotated.
- the carrier is held yieldingly upward by a spring 176, as shown in Figs. 3 and 19.
- the two stops 171 171 may be brought alternately into the path of the lingers 17 O of the rods 162 163.
- the sockets or flattened places 168 of each of the rods 162 163 are quartered with relation to each other, so that in order to render the pins 161 active in succession it is necessary to give each shaft at the proper time a quarter of a rotation. Therefore when the carrier 172 is depressed, so as to bring a stop 171 into the path of a finger 170, the stop holds the finger and the rod against rotation so long as the carrier is depressed.
- each shaft is therefore provided with a series of cams 177 177 177 177, arranged at an angle of ninety degrees relatively to each other, as shown in Figs. 19 and 20 and 2 1 and 26.
- each of the stops 171 has a cam 178, and the carrier 172 may be rotated to bring a cam 178 into the vertical plane of any one of the cams 177 177", &c.
- the two cams 178 on the stops 171 are in line with each other, so that when the carrier 17 2 is rotated in one direction one of the cams 178 rides up on the box 124:, the cam on the other stop being thereby moved to active position with relation to the cams on the shaft 150, and that when the carrier is rotated in the other direction the other cam 178 rides on the box 125, which thereby serves to lift it to an inactive position with relation to the cams and the finger on the rod 163. It will be further observed that by gradually rotating the carrier 172 with a step-by-step movement first in a direction opposite the movement of the hands of a watch in Fig.
- the cam 178 on one stop is brought into alinement with the cams 177, 177, 177", and 177 on the rod 162, and then the cam 178 on the other stop is brought suc cessively into alinement with the cams on the rod 163.
- the carrier is depressed and rotated to proper position, comes into line with the finger 170 it checks the rotation of the rod 162 or 163, as the case may be, and holds it until one of the cams 177, 177 177", or 177 engages the cam 178 on the said stop and throws it upward, so as to release the linger from the said stop and permit the finger and the rod to again rotate with the shaft.
- the linger 170 is shown as retarded by the stop 171.
- the controller comprising the carrier and stops and cams carried thereby, the shaft 173, and the handle 175.
- the rods 162 163 may be retarded to cause the coaction of the several pairs of gears by their respective clutches in proper order to drive the shaft 150 at six different speeds in succession, and by oppositely manipulating the controller the speed of rotation of the shaft 150 may be decreased step by step until it is driven at its lowest speed or its rotation is stopped, as when all of the clutchpins are in inactive position.
- the clutch-pin 161, carried by the gear 156 should be dropped to an inactive position, so
- .T/zc wart/Ia CZ'NZC/lfjhfl ildll shaft 150 carries in addition to the gears hereinbefore referred to another gear 180, which is pinned thereto.
- This gear intermeshes with a large gear 181, which is loose upon the intermediate shaft 182.
- This last-mentioned shaft 182 is the one which carries the spiral gear 107, intermeshing with and driving the gear 108, hereinbefore re- 'ferred to.
- Said shaft carries in addition to the loose gear 181.
- a gear 183 intermeshing with and driven by the gear 156.
- Each of the two gears 181 and 183 is provided with a frietion-surface on the interior of its rim, whereby it may be engaged frictionally by a double clutch 18a, pinned to the shaft and adapted to slide thereon.
- the difference in speed of retation of the spindle effected by clutching the gears 181 183 to the shaft is relatively great or equal to the range or difference in speed of the whole set of ratchet or auxiliary clutches.
- the clutch 181 may be moved in one direction or the other to connect the shaft to the two gears alternately by a rod 188, passed into the shaft, which is hollow for this purpose.
- gear 156 and the gear 180 are both fast upon the shaft 150 it is apparent that any one of the six speeds at which the shaft 150 is driven may be multiplied by two in transmission to the shaft 182, so that said shaft may be driven at any one of twelve different speeds from the two gears 156 and 180, according to the posi tion of the main double clutch 18 Rea-e1awe-gram); g. *The shaft 182 has mounted loosely upon it a gear 190, which intermeshes with the gear 129 on the spindle.
- the two gears 190 191 have friction-surfaces on the interior of their rims adapted to be alternately engaged by complemental friction-surfaces on a double clutch 194, pinned to the shaft 182 by a pin 195 passing through a slot in the said shaft into the hub of the clutch.
- the gear 191 is held against the shoulder or flange 186 and is spaced from the gear 190 by the pins 196 passed through apertures in the hub of the clutch and arranged inadirection parallel to the axis thereof.
- the pin 195 which, as has been stated, secured to the clutch, there is a rod 197 placed inside of the hollow shaft 182.
- This rod is similar to that at 188, as previously described, and it is adapted to be moved longitudinally to cause the clutching of the shaft 188 to the gear 190 or the gear 191 to effect the rotation of the spindle either in one direction or the other.
- the mechanism for moving these rods is similar, so that by describing that utilized for operating the rod 197 it will suffice for the other likewise.
- the rod 197 is shown as being hollow at its extreme end to receive a longi tudinally-slidable pin 198, splined within the rod by a spline 199.
- This pin is connected to areversingcontroller 200, which consists of a lever fulcrumed on a bracket 201, as shown in Fig. 1.
- the pin 198 is moved longitudinally within the rod 197.
- Screwed upon the shaft 182 are two abutments 202 203, socketed to receive the ends of two dogs 204:, which are oppositely arranged so that one dog bears against the abutment 202 and the other bears against the abutment 203.
- Bl/(JZ' mw'mp 'lhe shaft 182 is provided with a fifth gear, which is indicated at 210 and which is adapted to be driven through the medium of the back-gear shaft 211.
- the back-gear shaft is in substantially the same horizontal plane as the reversing-shaft 193, as shown in said figures.
- a pinion 21 1 which intermeshes with and drives said gear 210, and said shaft is rotated "from the shaft 150 by a train of gears comprising a pinion 213, pinned to the shaft 150, an idler-gear 2131, loose on a stud-shaft 21b2, projecting inwardly from one of the supports, and a large gear 212 on the shaft 211.
- the gear 210 is rotated so long as the shaft 150 is actuated.
- the gear 210 is rotated constantly so long as the shaft 150 is actuated.
- a ratchet-clutch is utilized for connecting the gear 210 with the shaft 182.
- This clutch mechanism is automatic, as illustrated in de- Now by movingthe pin 198 to the right,
- tail in Figs. 33 and 34 It includes a wheel 215, keyed to the shaft and having on its rim a ratchet 216, which extends under the rim of the wheel 210.
- the rim of the wheel 210 is socketed at 217 for the reception of a pawl 218, said pawl having a rounding end adapted to fit in the rounded end of the socket 217.
- a friction-plate 219 which extends into the space between the ratchet 216 and the inner face of the gear 210. hen the ratchet 216 is rotating more rapidly than the gear 210, this friction-plate by its connection with the pawl throws the pawl into the dotted position in Fig.
- the double clutch 184 In order that the back gear may be effective, the double clutch 184, hereinbefore described,(see Fig. 16,)should be in a neutral position, with the pin 198 (see Fig. 17) halfway between its limits of movement and with both dogs 204C inactive. This neutral posi tion of the clutch 184 would, if the back gear mechanism Were not provided, permit a cessation of rotation of the shaft 182; but inasmuch as the gear 210 is constantly rotated from the shaft 150 the movement of the double clutch 184 to neutral position simply permits the ratchet-wheel 215 to slow down until it is picked up by the pawl and caused to rotate at a slow speed synchronously with the gear 210.
- the clutch 181 may be denominated the baclcgear clutch, and the controller-lcver 189 may be termed the backgear controller.
- the back gear performs the usual function of effecting the rotation of the spindle at a reduced speed and with correspondingly greater power; but inasmuch as the shaft 150 may be driven at any one of six speeds, as hereinbefore stated, it is evident that by throwing in the back gear the shaft 182 may be driven at six relatively slower speeds or at any one of eighteen speeds in all.
- Each pair of inter-meshing gears on the two shafts 122 150 may be termed a couple of rotation, and it will be observed that of two adjacent couples of rotation the corresponding members of said couples are respectively fixed to and loose on the shafts, so that one member of each couple is loose on its shaft and the other member is fast on its shaft.
- the entire specd-varying mechanism is mounted in the head, which is shallow and pan-shaped, so that the gearing is all located in the same horizontal plane, and the head movable on the ways, so as to traverse the work-carrying spindle relatively to the tools.
- the differential gearing is particularly designed for the lathe and is exceedingly compact.
- transversely-movable spindle In my previous patent, No. 635,888, there is shown a latcrallymovable workholder, which there takes the form of a plate. This plate requires controlling-gibs at its periphery, making it necessary to rotate it at slow speeds, such as used in turning work of a large diameter. It is mounted in a frame or head, which in turn is supported by a special form of bed which afl'ords guides, one arranged above and the other below the axis of rotation of said plate. The end of the bed extends upward to furnish a firm backing for the head or frame. This type of bed and head makes impracticable the use of a long spindle, which depends for its stability on two separated bearings relatively near its ends.
- the present invention has for one of its objects to provide an improved lathe having a transversely-movable work-holder, in which the work-holder may be rotated at the high speeds that are considered as highly desirable in modern machine-shop practice.
- this object 1 have provided in lieu of the work-holding plate a relatively long spindle with separated bearings or bearings at or near its ends, and this necessitates a change in the bed and head structures to enable them to maintain a stable control and make possible the lateral feeding without change in the direction of the axis of the work.
- the guides for the head were therefore in the embodi ment of the invention herein illustrated both arranged substantially below the spindlebearings.
- a head-stock comprising a shallow pan-shaped casing which forms a receptacle for lubricant and a removable cover for said casing, in combination with a spindle and dilii'erential gearing therefor journaled in said head-stock and arranged to be partially immersed'in said lubricant.
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Description
PATENTED JUNE 20, I905. J. HARTNESS. METAL WORKING MACHINE.
APPLIOATION FILED JULY 27,1903.
12 SHEET8BHEET l.
PATENTED JUNE 20, 1905. J. HARTNBSS.
METAL WORKING MACHINE.
APPLICATION FILED JULY 27,1908.
12 SHEETS-SHEET 2.
PATENTED JUNE 20, 1905.
J. HARTNESS. METAL WORKING MACHINE APPLICATION FILED JULY 27,1903.
12 SHEETS-SHEET 3.
Invenibr -6 PATENTBD JUNE 20, 1905.
J. HARTNESS. METAL WORKING MACHINE.
APPLICATION FILED JULY 27,1903.
12 SHEETS-SHEET 4.
w M4 m PATENTED JUNE 20, 1905.
J. HARTNESS. METAL WORKING MACHINE.
APPLICATION FILED JULY 27.1903.
12 SHEETS-SHEET 5.
PATENTED JUNE 20, 1905. J. HARTNESS. METAL WORKING MACHINE.
APPLICATION FILED JULY 27,1903.
12 SHEETS-SHEET 6.
PATENTED JUNE 20, 1905. J. HARTNESS. METAL WORKING MACHINE. APPLICATION FILED JULY 27,1903.
12 sums-sum PA'TENTED JUNE 20, 1905.
J. HARTNESS. METAL WORKING MACHINE.
APPLICATION FILED JULY 27,1903.
12 SHEETS-SHEET a.
N a NQ PATENTED JUNE 20, 1905.
J. HARTNESS. METAL WORKING MACHINE. APPLICATION FILED JULY 27,1903.
12 SHEETSSHEET 9 3 g Q Q 5 n 1...... .0 t %m No; 792,591. PATENTED JUNE 20, 1905. J. HARTNESS. METAL WORKING MAGHINB.
APPLIOATION FILED JULY 27,1903.
No. 792,591. PATEN'I'ED JUNE 20, 1905.
J. HARTNBSS. METAL WORKING MACHINE.
12 SHEETS-SHEET 11 APPLICATION FILED JULY 27,1903- wiinasses: #W M; .XW;
PATENTED JUNE 20, 1905.
J. HARTNESS. METAL WORKING MACHINE.
APPLICATION FILED JULY 27,1903,
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UNTTED STATES 1 atented June 20, 1905.
PATENT ErcE.
I METAL-WORKING MACHINE.
SPECIFICATION forming part of Letters Patent No. 792,591 1, dated June 20, 1905.
Application filed July 27.1903. Serial No. 167,068.
To rtZJ/ whom, it may concern.-
Be it known that I, JAMES HARTNESS, of Springfield, in the county of WVindsor and State of Vermont, have invented certain new and useful Improvements in Metal-VVorking Machines, of which the following is a specification.
This invention has relation to metal-working machinery, and while it is more particularly applicable to that class of machines in which the work is rotated relatively to the tool, yet it is well adapted for other classes of metal-working machinery.
The object of the invention is to provide, first, a head having power-transmitting mechanism for effecting a differential rotation of the spindle from a constantly-rotated powershaft, with controlling means whereby the speed of rotation of the spindle may be graded from a relatively low speed to a relatively.
high speed, and vice versa.
Other objects of the invention are to provide for the power-transmitting gearing being all inclosed in the casing or head, which is preferably pan-shaped, with a removable cover; to provide for a transverse movement of the head and spindle relatively to the bed upon which it is supported; to provide automatic stopping mechanism for the head; to provide a single controller for the various positive or auxiliary clutches forming a part of the power-transmitting mechanism for the spindle; to provide for the simplification of the controlling mechanism and the powertransmittinguieclianism, and to provide certain other improvements, as will be hereinafter set forth in detail, and pointed out in the appended claims.
Referring to the accompanying drawings, Figure 1 represents in side elevation the head end of a metal-working lathe, preferably of the type in which a turret carries the tools to operate upon the work. In this figure shaft 122 is broken off and pulley 123 is omit-ted. Fig. 1 shows in side elevation a lathe enibodying the invention. Fig. 1" represents a plan view of the same. Fig. 2 represents an end elevation, of the head of the machine. Fig. 3 represents a partial section transversely through the bed from front to rear. Fig. 4:
represents a plan view of a portion of the head end of the bed with the head removed. Figs. 5, 6, 7, and 8 represent in detail the stopping mechanism for controlling the transverse movement of the head. Fig. 9 represents the gearing for actuating the feedingscrew for the head, said gearing being detached. Fig. 10 is a partial section through the machine from front to rear and represents the mechanism for controlling the worm by which power is imparted to the feed-screw for the head. Fig. 11 represents a front elevation of the gearing shown in Fig. 9. Figs. 12 and 13 illustrate the movable double worm for the feed-screw for the head. Fig. 14: represents in plan view the head end of the machine, with the top of the head removed to show the power-transmitting mechanism contained therein. Fig. 15 represents a section through the head end of the machine. Fig. 16 represents a horizontal section through the head in a plane coincident with the axis of the spindle. Fig. 17 represents an enlarged longitudinal section of the controller for one of the friction-clutches, which may be termed the reversing-gears in the head. Fig. 18 represents an enlarged section on the same plane as that on which Fig. 16 is taken and illustrates the single controller for the differential ratchet mechanism. Figs. 19 and 20 illustrate the controller in different positions. Fig. 21 represents a view of the controller detached and looking at its under side or face. Figs. 22 and 23 illustrate the operation of the controller. Fig. 24: represents a perspective view of the end of the powershaft. Fig. 25 represents the member in said shaft which controls the clutch-pin. Fig. 26 represents the end of the shaft and the rod or member in their operative relation. Fig. 27 is a section on the line 27 27 of Fig. 16. Fig. 28 represents a similar section through two of the gears or ratchet-clutches. Fig. 29 represents one of the ratchet-clutches in perspective view. Fig. 30 represents a section through one of said clutches. 'Figs. 31 and 32 represent the two members of one of the ratchet-clutches. Figs. 33 and 34: represent the ratchet-clutch on the back gear. Fig. 35 represents a section on the line 35 35 of Fig.
14. Fig. 36 represents a section on the line 36 36 of Fig. 14.
It will be understood that the present invention may be embodied in a turret-lathe such as set forth in Letters Patent No. 15 7,967, granted to me August 18, 1891, in which there is a carriage 10, movable longitudinally on the bed, a feedrod 70 for effecting the movement of the carriage, a turret 4L1 on the carriage, automatic stops (not illustrated) for the carriage, and other features forming a part of the lathe.
T/m fim/(L 'fhe lathe-bed is indicated at and has the usual ways or shears 12 for the turret-carriage. At the head end it is provided with forwardly and rearwardly extending portions 51 52, which are provided with parallel ways, guides, or shears 54: at a right angle to the ways for the turret-carriage. These guides or shears extend from front to rear transversely of the bed to receive a movable head which contains the spindle and the power-transmitting mechanism therefor. Said head comprises a panshaped casing and a top or cover This pan-shaped head is relatively shallow and is adapted for the reception of a quantity of lubricant in which the lower portions of the inclosed bearings and trains of gearing may be immersed to insure a thorough lubrication thereof when in operation. The top or cover prevents the escape of the lubricant and is readily removed to admit of a conveni ent inspection of the gearing while running and the adjustment and repair of the parts when at rest. The casing 55 is provided at its bottom with gibs 58 for taking under the ways or shears 53 54, some of the gibs being provided with adjusting-screws .(Zm0)'/i// n/ecluii/nz'sni. The head is provided with a downwardly-projecting portion which forms a nut 60 (see Figs. 3 and 4) for operative engagement with the threads of a feed-screw 61, arranged transversely of the bed between the guides or shears. This feedscrew, as shown in Fig. at, is journaled at one end in a bracket 62 on the bed and at its other end in a bracket 63, projecting forwardly and upwardly from the front of the bed. The forwardly-projecting end of the feed-screw is equipped with a wheel 64, having handles or spokes by which it may be rotated manually to feed the head transversely of the bed in a horizontal direction. In addition to the handwheel there are also power appliances for effecting the rotation of the feed-screw. These appliances comprise a worm-wheel 65, fast upon the feed-screw 61, a double worm 66 on an inclined shaft 67, having a spiral gear 68 intermeshing with and driven by a complemental gear 69 on a shaft 70, arranged longitudinally of the machine and journaled in a bearing 71 on the front of the bed 52, near the lower end thereof. This shaft 70 is utilized as the feed-shaft for the tool-carriage and extends along the bed, as shown in Fig. 1 and as described in Patent No. 457,967.
Referring now to the double worm, (shown in Figs. 9 to 13, inclusive) it will be observed that it is keyed upon the shaft 67 so as to slide thereon, its ends being held between the arms of a yoke 72. livoted to the yoke there is a latch 73, having notches 74L 75, adapted to be engaged with one of the upright walls forming the inner end of the extension 51, which is slotted for this purpose. This wall for convenience is numbered 76. By lifting the latch, which is provided with a handle 77 for this purpose, the yoke 72 may be moved longitudinally of the shaft 67 to engage either end of the double worm with the worm-wlmel 65. The threads on the opposite ends of the worm are relatively rightand left, so that the worm may be shifted to one position or the other in order to feed the head either forward or backward, as desired. The lower end of the shaft 67 is rotatively mounted in a knob 78, journaled on the bearing 71, so that the shaft 67 is adapted to oscillate about the axis of the knob to permit the worm to be moved into and out of engagement with the wormwheel.
Journaled in the :front of the extension 51 of the bed is a stud-shaft 79, having ahandle 80. This stud-shaft is provided with an cecentric 81, so that when the shaft is rocked the yoke, which rests upon the eccentric, may be moved toward and from the feed-screw (51 and the worm-wheel thereon. Thehandle 80 of the shaft 79, which serves to raise and lower the yoke and the double worm, and the handle 77 of the latch 73 are exposed in the front of the lathe, so that they may be easily manipulated by the operator, as shown in Fig. 3.
len/macho stop for the /2/mz(Z.For the pu r-' pose of automatically stopping the movement of the head in either direction there are a plurality of adjustable stop-bars, (indicated at 82 82, see Figs. 1 to 8.) These stop-bars are arranged side by side in a trough or groove in the top of the bed, and they extend from the front to the rear of the bed beneath the head. Between the several stop bars are placed thin strips of spacers 83. The bars may be all clamped together in the groove or trough 84 by a set-screw 85, a pin 86, (shown in dotted lines in Fig. st and having a beveled end,) and a complcmental pin 87, having a beveled end arranged at right angles to the pin 86, with its end projecting into the trough, so as to bear against the adjacent spacer 83. Each of the stop-bars 82 is provided with a recess 88 in its top edge or surface, the walls 89 90 of said recess being beveled to constitute a stop for coaction with a stop on the head. These several stop-bars may be adjusted longitudinally, and there are as many of them as maybe desired, six being illustrated in different relative positions.
The stop on the head consists of a double pawl 91, arranged yieldingly upon a shaft 92, journaled in the end walls of the head, so as to extend in lines parallel to the spindle. This shaft 92 is provided with a handle 93, (see Figs. 3 and 5,) and it is adapted to be movedlongitudinally of its axis and transversely of the stop-bars 82. The bottom wall of the head is socketed for the reception of the pawl, which is pinned to the shaft 92 by a pin 94. (See Fig. 8.) This pin bears against a spring 95, held in place in the end of the pawl by a screw 96. The diametrically opposite pin 97 is seated against the tension of a spring 98 in a socket in the pawl. The aperture 99 in the pawl, through which the shaft 92 passes, is in the form of an elongated slot, so as to permit a limited movement of the pawl transversely of the said shaft against the tension of the spring 95 or spring 98.
The walls of the recess 100 in the bottom wall of the head are such that when the pawl is rocked to the position shown in Figs. 7 and S, for instance, or to that shown in Fig. 6 they form an abutment for the non-acting end of the pawl. The shaft 92 is located above the stop-bars 82, so that by rocking it either end of the pawl may be caused to drop into one of the notches in the stop-bar, this being accomplished manually in the illustrated embodiment of the invention. The feed-shaft is frictionally driven, as will be explained, so that as soon as the pawl engages one of the inclined walls (or shoulders, as they may be termed) 89 90 on one of the stop-bars the head will be positively held against movement as soon as the inactive end of the pawl comes into engagement with one of the walls in the recess 100, or the operator may by oscillating the handle drop the double worm to an inactive position as soon as he observes that the pawl has engaged the shoulder upon the stop-bar. By moving the shaft 92 longitudinally the double pawl may be brought into the vertical plane of any one of the six stop-bars. Consequently the operation may effect the stopping of the head in either direction in any predetermined position thatmay be desired. Any convenient form of multiple stop may be used in lieu of that shown. By thus providingfor the lateral or transverse movement of the head the work may be shifted with relation to the turning or other tool which is operating upon the work. This is of advantage in many kinds of work and obviates the necessity of mounting a cross-slide upon the turret to the exclusion of other tools which it may be desired to use, since such cross-slides require a considerable amount of space upon the turret. The movable head likewise enables the work to be fed against a cutting-off tool or against a general shaping or face tool when their use is necessary, and which may be mounted stationarily upon the turret or upon some part of the bed.
Feed-shaft and friction-gearing therefm".-Tl16 feed-shaft 70, from which power is transmitted to the feed-screw for the head, is driven frictionally, being providedwith oppositely-beveled friction-disks 101 102, which are engaged with complemental driving-disks 103 104:, mounted upon a shaft 105, journaled in a yoke 106. This yoke is in turn journaled upon a shaft 182, which projects from the head, as will be explained. The shaft 182 is equipped with a spiral gear 107, intermeshing with and driving a complemental gear 108 on a shaft 109, journaled in bearings on the yoke 106, as illustrated in Fig. 2. The said shaft 109 carries at its lower end a spiral gear 110, intermeshing with and driving a complemental gear 111 on the shaft 105.
The yoke 106 may be swung about its fulcrum to move the driving friction-wheels 103 10 1 toward the axis of the shaft or away therefrom to cause engagement or disengagement of the disks 103 10 1 and disks 101 102. To this end there is secured upon a stud-shaft 112, arranged in the rear of the yoke, a cam 113, engaging with a complemental cam 11% on the lower end of the yoke 106. Secured to the earn 113 or to the shaft 112 there is a lever 115, by which the shaft may be rocked and the cam oscillated to move the yoke 106, as will be readily understood. By reason of this construction and arrangement of parts the arm or lever 113 will remain in whatever position to which it is adjusted. This mechanism provides a convenient means for frictionally driving the feed-shaft for the toolcarriage and the screw-shaft for the head.
The spindle.Referring now to Fig. 16, the spindle and the journal-bearings therefor will be described. WVithin the casing of the head are secured uprights or supports 120 121, which serve to support the journal-boxes for the various shafts and for the spindle, which are arranged in the head.
The main driving-shaft is indicated at 122, and it projects at its end beyond the head for the reception of a belt-wheel 123, by which it may be rotated in one direction and at a constant speed. This shaft is journaled in boxes 124 124:, which are driven into the supports 120 121, and it is held against longitudinal movement by collars 125, rigidly secured thereto and bearing against said boxes. Each box tapers outwardly and is formed with ashoulder to bear against theinner face of the web or support 120 121, as the case may be. As the boxes for all of the various shafts are similar to the one described a detailed description will not be given of any of the others.
The spindle is indicated at 126. It consists of a hollow shaft having a smooth unshouldered periphery or exterior surface. In this respect it is essentially different from any of the spindles which have been heretofore used in metal-working machines. On its inner end it is equipped with a chuck 127.
IIC
The spindle is held against movement by the following devices: Secured to the spindle by two screw-pins 128 128 is the common hub of two gears 129 and 180. On one side of the gear 129 is a flange or web 131, which is cast with the casing or head, and between the said liange and the end of the hub of the wheel are two loose washers 132 133. On the opposite side of the gear 130 are two similar loose washers 13 1 and 135, and bearing upon the washer 135 are two set-screws 136 136, passed through ears or lugs 137, east integrally with the head. By adjusting these screws 136 136 the gears 129 130 may be clamped against axial movement and by reason of their pinned connection with the spindle hold said spindle against movement longitudinally of its axis. By the simple expedient of witlulrawving the screw-pins 128 128 the spindle may be removed as an entirety from the head by drawing upon the chuck end of it. At each end the spindle is mounted in boxes 138 138, which are exteriorly tapered and are set in the supports 120 121 in tapering apertures provided for their reception. Between the boxes and the shaft are placed bushings 139 110. To hold the boxes in place, strong helical s 'irings 1111 encircle the exterior cylindrical ends thereof and bear z'rgail'ist sluinilders on the bushings and also against the inner wall of the head. Each box or bearing is formed with a cavity 112 for the reception of lubricant and also for the reception of a loose ring 1413, which assists in carrying the lubricant to the'various parts of the bearing.
[)lif/iv'wni/(l/ gin/ow m lteferring to Figs. 1st to 36, inclusive, the mechanism for effecting a differential rotation of the spindle from the driving-shaft will now be described. It may be here explained that the object of this gearing is to provide for rotating the spindle at any one of a large number of speeds and for reversing it without varying the speed or direction of rotation of the driving-shaft. This gearing is so constructed that the spindle may be driven from the lowest speed to the highest speed by a series of steps, as it were, each increase in speed being twentylive per cent. over the previous speed. The speed variation is effected by clutch mechanisms, the finer gradations of speed being secured by positive ratchet-clutches with devices which insure their operation in proper sequence and the greater or coarser gradations being secured by main clutches. The entire range of the liner gradations in speed or the difference between the lowest speed and the highest speed secured by the ratchet-clutches is about equal to the range or difference in speed secured by the main clutches. In this way the lov-speed main clutch may be operated while the ratchet-clutches are operated from relatively low speed to relatively high speed, and then by throwing in the high-speed main clutch the ratchet-clutches may be again operated in sequence from relatively low to relatively high, with the result that the munber of fine gradations in speed are equal to the number of ratchet-clutches multiplied by the number of main clutches. In addition to this mechanism there is back gearing inclnding a back-gear clutch which can be operated coincidently with the ratchet-clutches for securing gradations of speed still lower than those secured by the use of the main clutches. There is likewise employed a reversing-gearing with a reversing-clutch, so that without changing the direction of rotation of the prime power-shaft the spindle may be driven in a reverse direction. This reverse-clutch may be operated in conjunction with the ratehet-clutches for effecting a dilierential speed. The spindle is provided with gears 129 130, as previously described, to which power is imparted by trains of gearing, as will be explained, for the purpose of driving the spindle in one direction or the other, these trains of gearing being interposed between the power-shaft 122 and the spindle. There are interposed between these two elements to wit, the 1 )ower-shaft and the spindle four shafts, which may be termed the secondary power-shaft, the back-gear shaft, an intermediate shaft, and a reverseshaft. The power-shaft, the secondary power-shaft, and the intermediate shaft all have their axes located in the same horizontal plane as the spindle, this plane being coincident with the plane of division between the bottom portion of the casing or head and the cover thereof,
shown in Figs. 15 and 16.
Rafa/mi (ifllfli/l/ wmc/m/iismr Tlle prime power-shaft 122 has pinned to it three gears 14st 1 15 1 16, which intermesb, respectively, with gears 117 M8 149, all loosely mounted upon the secondary power-shaft 150. There are likewise loose upon the power-shaft 122 the following gears 151, 152, and. 153, respectively intermeshing with the gears 154: 155 156, all of which a re pinned to the shaft 150. The pairs of intermeshing gears 116 and 1 19, 1 15 and 1 18, 1&4 and let? are in increasing ratios, as are the pairsof intermeshing gears 151 and 15 1, 153 and 156, and 152 and Consequently, as will be explained, the shaft 150 may be d rivcn at any one of six speeds relatively to the shaft 122, the ratios of the pairs of coacting gears being such that each increase in speed of the shaft 150 is twenty-live per cent. over the preceding speed. The gears 14:4, 145, and 1 16 all rotate in unison with the shaft 122, and therefore the gears 1 17, 1&8, and 119 are constantly in rotation loosely upon the shaft 150. Additional clutches are interposed between the last-1nentioned three gears andv the shaft 150, and similar clutches are interposed between the loose gears 151 152 153 and the shaft 122, these clutches providing for the liner gradation of speed of the spindle.
Each of the fast gears on each of the two shafts 122 carries a loose pawl 160, which is adapted to be thrust inward by a spring 1611, as shown in Fig. 30. This pawl is placed in a socket formed in a disk-like member carried by the gear and rests loosely upon a pin 161, arranged radially of the gear and passing through an aperture in the shaft. The two shafts are hollow for the reception of rotatable members or rods 162 163, against which the ends of the pins 161 bear.
Each of the loose gears 151, 152, and 153 on the shaft 122 and the gears 147, 148, and 149 on the shaft 50 is keyed to a sleeve or bushing 16 1, loose upon its respective shaft. This sleeve or bushing in each case is formed on its end with ratchet-teeth 165 and fits into a socket within the disk-like hub of the next adjacent gear, so that the ratchet-teeth arein a potential relation to the pawl 160, carried by said gear.
On the two shafts the fast and loose gears are mounted in pairs the fast gear 1 11, for instance, carrying a pawl adapted to engage the ratchet of the gear 151, the gear 1415 carrying a pawl for the ratchet-gear 152, and the gear 146 carrying a pawl for the ratchet of gear 153. The arrangement of the gears on the shaft 150 is similar to that just described, there being upon each shaft three pairs of gears having pawls and ratchets arranged in potential relation. This pawl -andratchet mechanism forms in each case a positive ratchet-clutch by which the loose gear may be positively keyed to the fastgear.
The pins 161 control the operation of the various pawls 160, mechanism being provided by which these pins are moved into and out of active or inactive position, as the case may be, said mechanism being such that only one pin is active at a time and the pins are actuated in proper sequence.
The rotative members or rods 162 163 are held against longitudinal movement by setscrews 166, formed in an extension on theinner end of the casing or head, said set-screws being locked in place by additional set-screws 167, arranged at right angles thereto. Each rod 162 or 163 is provided with three recesses or sockets 168, into which the pin 161 may drop when permitted. These sockets are out of line with each other and may be formed by simply flattening the rod 162 163 or forming a short groove in the periphery thereof. The rod may be rotated as in the case of the rod 162, (shown in Fig. 16,) so that all of the pins 161 will bear against the rounded periphery of the rod and be held in an inactive position; but each rod may be rotated so as to bring a socket 168 under one of the pins 161, as shown in the case of the rod 163 at the left end thereof, where the pin 161, carried by the gear 154:, is shown as dropped into a socket, so as to permit the pawl to engage the teeth of the ratchet of the gear 1 17. Consequently the shaft 150 may by properly rotatively adjusting the rods 162 and 163 be driven at any one of six speeds from the shaft 122. A controller is provided for eifecting the relative rotation of these rods and is so constructed that the clutchpins 161 are permitted to drop into active position in a predetermined order, beginning with the coacting gears having the lowest ratio and ending with that pair of gears having the greatest ratio-to wit, those indicated at 153 and 156-whereby the shaft 150 is driven gradually from its lowest to its highest speed, the increment of increase being twenty-five per cent. over the preceding rate of speed. The controller for the rods 162 163 is best shown in Figs. 18 to 26, inclusive. Each of the rods 162 163 is formed with a finger 170, adapted to be engaged by an abutment 171. These two abutments constitute stops hinged to a carrier 172. This carrier is secured to an upright shaft 173, journaled in the extension 171 of the head or casing, and is equipped on its end with a handle 175, by which it may be depressed and rotated.
The carrier is held yieldingly upward by a spring 176, as shown in Figs. 3 and 19. The two stops 171 171 may be brought alternately into the path of the lingers 17 O of the rods 162 163. (See Fig. 18.) The sockets or flattened places 168 of each of the rods 162 163 are quartered with relation to each other, so that in order to render the pins 161 active in succession it is necessary to give each shaft at the proper time a quarter of a rotation. Therefore when the carrier 172 is depressed, so as to bring a stop 171 into the path of a finger 170, the stop holds the finger and the rod against rotation so long as the carrier is depressed. Consequently mechanism must be provided for throwing the stop to an inoperative position as soon as the rotation of the rod has been retarded a predetermined length of time, so as to effect a relative rotation of the rod and its shaft ninety degrees, one hundred and eighty degrees, or two hundred and seventy degrees.
It should be remembered that the rods are simply frictionally mounted within the shafts 122 and 150 and normally rotate with them, unless retarded to effect their relative rotation. Each shaft is therefore provided with a series of cams 177 177 177 177, arranged at an angle of ninety degrees relatively to each other, as shown in Figs. 19 and 20 and 2 1 and 26. For coaction with these cams separately each of the stops 171 has a cam 178, and the carrier 172 may be rotated to bring a cam 178 into the vertical plane of any one of the cams 177 177", &c.
It will be observed that the two cams 178 on the stops 171 are in line with each other, so that when the carrier 17 2 is rotated in one direction one of the cams 178 rides up on the box 124:, the cam on the other stop being thereby moved to active position with relation to the cams on the shaft 150, and that when the carrier is rotated in the other direction the other cam 178 rides on the box 125, which thereby serves to lift it to an inactive position with relation to the cams and the finger on the rod 163. It will be further observed that by gradually rotating the carrier 172 with a step-by-step movement first in a direction opposite the movement of the hands of a watch in Fig. 18 and then in the opposite direction, or with the movement of the hands of a watch, the cam 178 on one stop is brought into alinement with the cams 177, 177, 177", and 177 on the rod 162, and then the cam 178 on the other stop is brought suc cessively into alinement with the cams on the rod 163. As each stop, when the carrier is depressed and rotated to proper position, comes into line with the finger 170 it checks the rotation of the rod 162 or 163, as the case may be, and holds it until one of the cams 177, 177 177", or 177 engages the cam 178 on the said stop and throws it upward, so as to release the linger from the said stop and permit the finger and the rod to again rotate with the shaft.
in Fig. 20, at the right-hand side, the linger 170 is shown as retarded by the stop 171. Now when the proper cameomes around--as, for instance, earn 177 in Fig. 23*it engages the cam 178 and lifts it and the stop, so as to permit the linger to rotate.- Therefore by properly depressing and manipulating the controller (comprising the carrier and stops and cams carried thereby, the shaft 173, and the handle 175) the rods 162 163 may be retarded to cause the coaction of the several pairs of gears by their respective clutches in proper order to drive the shaft 150 at six different speeds in succession, and by oppositely manipulating the controller the speed of rotation of the shaft 150 may be decreased step by step until it is driven at its lowest speed or its rotation is stopped, as when all of the clutchpins are in inactive position. In order to start the gearing, however, it is necessary that the clutch-pin 161, carried by the gear 156, should be dropped to an inactive position, so
to clutch the gear 1 19 with the shaft 150.
.T/zc wart/Ia CZ'NZC/lfjhfl ildll shaft 150 carries in addition to the gears hereinbefore referred to another gear 180, which is pinned thereto. This gear intermeshes with a large gear 181, which is loose upon the intermediate shaft 182. This last-mentioned shaft 182 is the one which carries the spiral gear 107, intermeshing with and driving the gear 108, hereinbefore re- 'ferred to. Said shaft carries in addition to the loose gear 181. a gear 183, intermeshing with and driven by the gear 156. Each of the two gears 181 and 183 is provided with a frietion-surface on the interior of its rim, whereby it may be engaged frictionally by a double clutch 18a, pinned to the shaft and adapted to slide thereon. The difference in speed of retation of the spindle effected by clutching the gears 181 183 to the shaft is relatively great or equal to the range or difference in speed of the whole set of ratchet or auxiliary clutches.
Passing tl'u'ough the hub of the clutch 184, so as to lie parallel to the axis thereof, are pins 185, which bear against hubs of the gears 181 183 to hold them against movement relatively to each other,said gears being held against outward movement by a flange 186 on the shaft and by a collar 187, pinned thereto.
The clutch 181 may be moved in one direction or the other to connect the shaft to the two gears alternately by a rod 188, passed into the shaft, which is hollow for this purpose.
The mechanism by means of which the rod 188 is moved will be subsequently described, it being sufficient at the present time to state that it is effected by means of a lever 189, as shown in Fig. 3, and devices interposed between said lever and said rod. By moving the lever in one direction the gear 181 is clutched to the shaft, and by moving it in the opposite direction the gear 183 is clutched to the shaft. Therefore inasmuch as the gear 156 and the gear 180 are both fast upon the shaft 150 it is apparent that any one of the six speeds at which the shaft 150 is driven may be multiplied by two in transmission to the shaft 182, so that said shaft may be driven at any one of twelve different speeds from the two gears 156 and 180, according to the posi tion of the main double clutch 18 Rea-e1awe-gram); g. *The shaft 182 has mounted loosely upon it a gear 190, which intermeshes with the gear 129 on the spindle. These two gears are utilized for rotating the spindle in the usual direction; but for the purpose of reversing the rotation of the spindle the following train of gearing is utilized: Loose upon the shaft 182 is a gear 191, which intermeshes with a reversing-gear 192, keyed upon the reverse-shaft 193, mounted in boxes in the guides or uprights 120 121. (See Figs. 3and 1 1.) This gear 192 also intermeshes with the gear 130 on the spindle. The two gears 190 191 have friction-surfaces on the interior of their rims adapted to be alternately engaged by complemental friction-surfaces on a double clutch 194, pinned to the shaft 182 by a pin 195 passing through a slot in the said shaft into the hub of the clutch. The gear 191 is held against the shoulder or flange 186 and is spaced from the gear 190 by the pins 196 passed through apertures in the hub of the clutch and arranged inadirection parallel to the axis thereof. Connected to the pin 195, which, as has been stated, secured to the clutch, there is a rod 197 placed inside of the hollow shaft 182. This rod is similar to that at 188, as previously described, and it is adapted to be moved longitudinally to cause the clutching of the shaft 188 to the gear 190 or the gear 191 to effect the rotation of the spindle either in one direction or the other. As has been stated, the mechanism for moving these rods is similar, so that by describing that utilized for operating the rod 197 it will suffice for the other likewise.
In Fig. 17 the rod 197 is shown as being hollow at its extreme end to receive a longi tudinally-slidable pin 198, splined within the rod by a spline 199. This pin is connected to areversingcontroller 200, which consists of a lever fulcrumed on a bracket 201, as shown in Fig. 1. By swinging the lever in one direction or the other the pin 198 is moved longitudinally within the rod 197. Screwed upon the shaft 182 are two abutments 202 203, socketed to receive the ends of two dogs 204:, which are oppositely arranged so that one dog bears against the abutment 202 and the other bears against the abutment 203. These abutments are held securely against longitudinal movement by collars 205 and set-screws 206. The dogs project through slots in the shaft 182 and the rod 197, so that their inner ends bear against the pin 198, which is formed with cam-shoulders 207 207. Each dog 204 bears at one end against the abutment 203 and is cam-shaped at its other end, so as to bear against the end of the slot in therod 197. as shown in Fig. 17, one dog 204 is thrust outward, and by reason of its location, as described, the rod 197 is thrust to the right by a cam action of the end of the dog thereon. By moving the pin 198 to the left the cam-shoulder 207 will engage the cam end of the other dog and thrust it outward, the first-mentioned dog dropping to an inactive position. This effects a movement of the rod 197'in the opposite direction. Therefore an oscillation of the lever 200 in one direction or the other effects the clutching of the shaft 182 to the spindle 126, so as to rotate it either in one direction or the other.
Bl/(JZ' mw'mp 'lhe shaft 182 is provided with a fifth gear, which is indicated at 210 and which is adapted to be driven through the medium of the back-gear shaft 211. (See Figs. 11, 15, 35, and The back-gear shaft is in substantially the same horizontal plane as the reversing-shaft 193, as shown in said figures. It is provided with a pinion 21 1, which intermeshes with and drives said gear 210, and said shaft is rotated "from the shaft 150 by a train of gears comprising a pinion 213, pinned to the shaft 150, an idler-gear 2131, loose on a stud-shaft 21b2, projecting inwardly from one of the supports, and a large gear 212 on the shaft 211. In view of this construction the gear 210 is rotated so long as the shaft 150 is actuated. By virtue of this construction the gear 210 is rotated constantly so long as the shaft 150 is actuated.
A ratchet-clutch is utilized for connecting the gear 210 with the shaft 182. This clutch mechanism is automatic, as illustrated in de- Now by movingthe pin 198 to the right,
tail in Figs. 33 and 34. It includes a wheel 215, keyed to the shaft and having on its rim a ratchet 216, which extends under the rim of the wheel 210. The rim of the wheel 210 is socketed at 217 for the reception of a pawl 218, said pawl having a rounding end adapted to fit in the rounded end of the socket 217. To the inner edge of the pawl is secured a friction-plate 219,which extends into the space between the ratchet 216 and the inner face of the gear 210. hen the ratchet 216 is rotating more rapidly than the gear 210, this friction-plate by its connection with the pawl throws the pawl into the dotted position in Fig. 16"; but when the speed of the ratchet is less than that of the gear 210 the said friction-plate causes the ratchet to be thrown outward to the full-line position in the last-mentioned figure by reason of the frictional engagement of said plate with the inner face of the ratchet 216. A spring 220 insures the frictional engagement of the plate with the inner face of the ratchet. The advantage of this construction over the ordinary lazy-pawl arrangement in which the pawl is adapted to engage the ratchet is that when the ratchet is driven at a higher rate of speed than the speed of rotation of the gear the pawl is antomatically moved out of engagement with the teeth, so as to preventits clatter-ing thereon. In order that the back gear may be effective, the double clutch 184, hereinbefore described,(see Fig. 16,)should be in a neutral position, with the pin 198 (see Fig. 17) halfway between its limits of movement and with both dogs 204C inactive. This neutral posi tion of the clutch 184 would, if the back gear mechanism Were not provided, permit a cessation of rotation of the shaft 182; but inasmuch as the gear 210 is constantly rotated from the shaft 150 the movement of the double clutch 184 to neutral position simply permits the ratchet-wheel 215 to slow down until it is picked up by the pawl and caused to rotate at a slow speed synchronously with the gear 210. Therefore the clutch 181 may be denominated the baclcgear clutch, and the controller-lcver 189 may be termed the backgear controller. The back gear performs the usual function of effecting the rotation of the spindle at a reduced speed and with correspondingly greater power; but inasmuch as the shaft 150 may be driven at any one of six speeds, as hereinbefore stated, it is evident that by throwing in the back gear the shaft 182 may be driven at six relatively slower speeds or at any one of eighteen speeds in all. Each pair of inter-meshing gears on the two shafts 122 150 may be termed a couple of rotation, and it will be observed that of two adjacent couples of rotation the corresponding members of said couples are respectively fixed to and loose on the shafts, so that one member of each couple is loose on its shaft and the other member is fast on its shaft.
ln connection with this arrangement it is possible, by means of the controlling mechanism, to alternately and positively cl uteh the corresponding members of the couples, whereby the member which is fast on the driving-shaft actuates the member which is fast on the driven shaft through the medium of either member of the same couple or the corresponding member of the other couple. It may be stated that the members of the couples of rotation are alternately fast and loose on the primary driving-shaft and the secondary driving-shaft. The advantage of a construction of this characteris unquestionably apparent to those skilled in the art to which this invention relates. vIt is possible for the operator to drive the spindle at practically any speed that may be desired.
The entire specd-varying mechanism is mounted in the head, which is shallow and pan-shaped, so that the gearing is all located in the same horizontal plane, and the head movable on the ways, so as to traverse the work-carrying spindle relatively to the tools. The differential gearing is particularly designed for the lathe and is exceedingly compact.
One of the most important features of the present invention is the transversely-movable spindle. In my previous patent, No. 635,888, there is shown a latcrallymovable workholder, which there takes the form of a plate. This plate requires controlling-gibs at its periphery, making it necessary to rotate it at slow speeds, such as used in turning work of a large diameter. It is mounted in a frame or head, which in turn is supported by a special form of bed which afl'ords guides, one arranged above and the other below the axis of rotation of said plate. The end of the bed extends upward to furnish a firm backing for the head or frame. This type of bed and head makes impracticable the use of a long spindle, which depends for its stability on two separated bearings relatively near its ends.
The present invention has for one of its objects to provide an improved lathe having a transversely-movable work-holder, in which the work-holder may be rotated at the high speeds that are considered as highly desirable in modern machine-shop practice. In attaining this object 1 have provided in lieu of the work-holding plate a relatively long spindle with separated bearings or bearings at or near its ends, and this necessitates a change in the bed and head structures to enable them to maintain a stable control and make possible the lateral feeding without change in the direction of the axis of the work. The guides for the head were therefore in the embodi ment of the invention herein illustrated both arranged substantially below the spindlebearings.
So far asI am aware, 1 am the first to have provided a metal-turning machine or lathe having a transversely-movable spindle which maintains the same axial direction of the work at all points in its feed. Hereto'fore it has always been considered by tool-builders that the head carrying the spindle should be rigid with the bed and that the tool alone should be moved. This involved placing one tool-slide upon another, so that the tool could be moved both longitudinally and laterallyrelatively of the work, the imposition of the cross-slide upon the sliding carriage making the entire structure frail. I. have found it to be simple and more practical to mount he tool on a single slide and to obtain the transverse motion by sliding the head, thus securing the ideallyproportioned slides in each case and providing the two necessary motions or lon gitudinal and lateral feed for turning and facing. 1n the present invention, inaddition, I have made it possible to secure the advantages of the two slides, one longitudinally movable to carry the tool and the other transversely movable to carry the work, and at the same time those ad vantages which accrue from the use of a spindle in work requiring high speed.
I. do not herein claim the differential gearing fir/2w, as it forms the subiectanatter of a copending application, Serial No. QZshSGS, iiled September 17, 1904.
Having thus explained the nature of the invention and described a way of constructing and using the same, although without attempting to set forth all of the forms in which ing, a driving-shaft, and differential gearing interposed between said shaft and said spindle, all arranged in substantially the same horizontal plane.
3. .ln a metal-working lathe, a head-stock comprising a shallow pan-shaped casing which forms a receptacle for lubricant and a removable cover for said casing, in combination with a spindle and dilii'erential gearing therefor journaled in said head-stock and arranged to be partially immersed'in said lubricant.
4:. In a metal-working lathe, a work-carryin g spindle, a power-shaft parallel therewith rotatable at a constant speed, and differential gearing interposed between said spindle and said shaft, all disposed in substantially the same horizontal plane, in combination with a
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16706803A US792591A (en) | 1903-07-27 | 1903-07-27 | Metal-working machine. |
US262419A US840322A (en) | 1903-07-27 | 1905-05-26 | Lathe-spindle. |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16706803A US792591A (en) | 1903-07-27 | 1903-07-27 | Metal-working machine. |
Publications (1)
Publication Number | Publication Date |
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US792591A true US792591A (en) | 1905-06-20 |
Family
ID=2861080
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US16706803A Expired - Lifetime US792591A (en) | 1903-07-27 | 1903-07-27 | Metal-working machine. |
Country Status (1)
Country | Link |
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US (1) | US792591A (en) |
-
1903
- 1903-07-27 US US16706803A patent/US792591A/en not_active Expired - Lifetime
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