US2647455A - Hydraulic apparatus - Google Patents

Description

4 Sheets-Sheet 1 Filed Feb. 24, 1947 INVENTOR.

I CECIL E. ADAMS Aug. 4, 1953 c. E. ADAMS HYDRAULIC APPARATUS 4 Sheets-Sheet 2 Filed Feb. 24, 1947 INVENTOR. CEOI L E. ADAMS Aug. 4, 1953 c. E. ADAMS HYDRAULIC APPARATUS 4 Sheets-Sheet 5 Filed Feb. 24, 1947 INVENTOR. SEC. E. ADAMS A 1953 c. E. ADAMS 2,647,455

HYDRAULIC APPARATUS File d Feb. 24, 1947 4 Sheets-Sheet 4 INVENTOR. CECIL E. ADAMS O BY Patented Aug. 4, 1953 HYDRAULIC APPARATUS Cecil E. Adams, Columbus, Ohio, assignor to The Denison Engineering Company,

Columbus,

Ohio, a corporation of Ohio Application February 24, 1947, Serial No. 730,504 I 6 Claims. (Cl. 1'00-137) This invention relates generally to hydraulic apparatus and is more specifically directed to a hydraulicaly actuated, stock-feeding attachment for hydraulic presses.

One of the objects of this invention is to provide a feeding mechanism. which will feed stock to a press or other device for performing an operation on the stock, which feeding mechanism will operate in timed sequence with the press and will uniformly accelerate and decelerate the stock in its movement thereby avoiding slippage between the feeding means. and the stock with consequent greater accuracy in the feeding operation.

Another object of the invention is to provide a feeding mechanism having a fluid motor and control valve mechanism therefor which will be operative to cause the fluid motor to perform separate feeding cycles of not more than one revolution in durationv spaced by inactive or rest periods in which the device served by the feeding mechanism performs an operation on the stock fed thereto.

A further object of the invention is to provide a feeding mechanism having a feed roll, a fluid motor and motion transmitting means therebetween which will provide for equal successive increments of rotation of the feed roll, the motion-transmitting means being adjustable to permit variation in the length of the increments of. rotation whereby more or less stock will be fed depending upon the operations being performed.

A still further object. of the invention is to provide a feeding mechanism havinga feed roll, a fluid motor and motion-transmitting means therebetween, the latter means includin a oneway clutch between the feed roll and driver therefor, a crank on the driver, an eccentric operated by the fluid motor, and a connecting rod between the eccentric and the crank, theelements being so arranged that rotation of the eccentric causes a back and forth rocking movement of the crank, the one-way clutch serving to transmit motion from the driver to the feed roll when the crank moves in one direction and to avoid the transmission of motion to the feed roll when the crank moves in the opposite direction.

Another object is to provide a combined hydraulic press and feeding mechanism having control mechanism which causes the automatic reciprocation of the ram of the press and the automatlc intermittent operation of the feeding mechanism, the operations of the devices being altert y p r m d to avoid int r er n e An object also is to provide a hydraulic system for the combined press and feeding mechamentioned in the preceding paragraph, the system having a source of fiuid pressure, a reversing valve responsive to fluid pressure for initiating the operation of the press, another valve device actuated by the press to direct fluid from the pressure source to the feeding mechanism and a third valve device operated by the driving motor of the feeding mechanism for applying fluid pressure to said reversing valve to start the operation of the press when a feeding operation has been concluded; this hydraulic system forms the subject matter of my divisional application Serial No. 65,461, filed December 15, 1948, now Patent No. 2,618,933 issued November 25, 1952.

Further objects and advantages of the persent invention will be apparent from the following description, reference being had to the accompanying drawings wherein a preferred form of embodiment of the invention is clearly shown.

In the drawings:

Fig. 1 is a perspective View of a feeding mechanism formed in accordance with the present invention showing the same attached to a press.

Fig. 2 is an end elevational view of the feeding mechanism shown in Fig. 1.

Figs. 3 and 4 are vertical sectional views taken through the feeding apparatus showing different features of construction.

Fig. 5 is a horizontal longitudinal sectional View taken through the feeding mechanism on the plane indicated by the line V-V of Fig. 4.

Fig. 6 is a diagrammatic view of the hydraulic system employed in the press and the feeding mechanism therefor.

I Referring more particularly to the drawings numeral 20 designates generally the feeding mechanism forming the subject matter of the present invention. This feeding mechanism may be used as an accessory on presses of various types, but for purposes of illustration, it is shown in the drawings as an accessory for a hydraulic press, this device being indicated generally by the numeral 2|. The press 2| includes a frame 22 having a bolster section 23, an upright column 24, and a head section 25, the head and bolster sections projecting forwardly from the column 2G. The head section has a power cylinder 26 supported therein, this cylinder receiving a piston 2'! from which a ram 28 projects toward the bolster section 23. When movement is transmitted to the piston 21 to cause reciprocation thereof in the cylinder 26, the ram 28 will be moved toward and away from the bolster section. The head section also receives a control valve 30 which may be of any suitable type, the one illustrated being of the type shown in my copendingapplication, Serial No. 600,736, filed June 21, 1945, now Patent No. 2,561,766. This valve, shown diagrammatically in Fig. 6, operates to control the flow of fluid from a pressure source 3| to the power cylinder 25 to secure the automatic operation of the piston and ram. The pressure source 3! includes a reservoir 32, a motor driven pump 33 and a relief valve 34, the latter being adjustable to vary the pressure in the hydraulic system at which the discharge from the pump 33 will be bypassed back to thereservoir 32. A fluid line 35 extends from the pressure source to the control valve 39, this fluid line being in open communication with the inlet port 36 of the valve 38. While this valve has been described in detail in the co-pending application above referred to, it will also be described herein sufficiently to facilitate the understanding of the present invention.

Valve includes a body casing 31, which is formed with a pair of vertically extending bores 38 and 48. Body 3? is also formed with a plurality of annular grooves 4| to 41, which are spaced longitudinally of, and open into, the bore 38. The body is further formed with annular grooves 48, 33, and 58, which are spaced longitudinally of, and open into, the bore 48. Bore 38 receives for sliding movement a spool 52 having an internal chamber 53 and a plurality of longitudinally spaced sets of ports 54 to 60, inclusive, formed in the side wall thereof. Certain of these ports register with certain of the grooves M to 4'! in various positions of movement of the spool 52 in the bore 38. The upper end of the chamber 53 is closed by a cap 62 in which a recess 63 is formed, this recess opening to the under side of the cap. The upper end of the coil spring 64 is received in the recess 63, the lower end of this spring being disposed in a socket 65 formed in a shuttle valve 66 disposed for sliding movement in the chamber 53 of spool 52. The shuttle valve 66 comprises a cylindrical member having an external groove 61 formed in the wall thereof, intermediate the ends of the cylinder, this groove providing spaced heads 68 and 10 on the spool. The shuttle valve is also provided at the head portion 63 with transversely extending ports ll which communicate at their inner ends with a chamber 72. Axial ports 13 and M are formed in the shuttle valve, the former extending from the chamber 12 to the socket 65 and the latter extending from the chamber 12" to the lower end of the shuttle valve. spring 63 normally retains the shuttle valve in its lowered position with the lower end thereof in engagement with the bottom wall of the chamber 53 in spool 52.

The spool 52 has a rod projecting from its lower end through a cap 16 secured to the bottom of the body 31!. This rod is connected at its lower end to another rod Ti commonly termed the shipper rod, this rod receiving a collar 18 which is adjustably secured to the rod and is engaged at certain stages of operation of the ram 28 by the end of an arm 83 secured for movement with the ram. When the ram moves in an upward direction and approaches the upper limit of its travel, the arm 86 will engage the collar 18 and move the rod H in an upward direction. This movement is transmitted by rod 15 to the spool 52 causing the latter to move to a position wherein fluid flow to the lower end of the power cylinder to effect upward movement of the ram The coil 4 will be interrupted. When this event occurs, the ram will come to rest in a raised, inoperative position ready for another cycle of operation. Ports 58 in spool 52 communicate at all times with groove 45, which is in open communication with the inlet port 36, thus fluid from the pressure source may flow through the ports 53 into the chamber 53 at the groove 61 formed in the shuttle valve. When the parts of the valve are in the position shown in Fig. 6, which position will be assumed when the ram 28 is at rest, fluid admitted to groove 61 may flow outwardly from the chamber 53 through ports 5'! into groove 44.

Body 31 has a drilled opening 8| formed in one side thereof, which opening communicates at its inner end with the groove 44 so that fluid admitted to the groove may flow from the groove through the inner portion of opening 8! to bore 40 and from the latter through the outer portion of opening 8| to a line 82. The fluid admitted to the bore 40 when the parts are in the positions shown in Fig. 6 is prevented from flowing longitudinally thereof by a spool 33 disposed for movement in the bore 48. This spool has longitudinally spaced heads 33 and which engage the side walls of the bore 48 and control communication between the portion of the bore 48 between heads 84 and 85 and the groove 49, head 84 serving at all times to prevent communication between that portion of the bore and the groove 48.

Normally, the spool 83 is yieldably retained in a centered position by coil springs 85 and 8'! dis posed at theends of the spool between the end caps for the body 31 and shoulders formed on the spool and a spring abutment 88. When in the centered position, under the influence of the springs, the space around the spool 83 between the heads 84 and 85 will be in communication with groove 46 surrounding bore 38. Groove 36 is connected, when the parts of the valve mechanism are in position to maintain the mechanism inoperative, with the reservoir 32 through ports 59 in spool 52, chamber 53, ports 69, grooves 31 and 59 and exhaust line 90, thus fluid under pump pressure will be bypassed directly to the reservoir 32 when the mechanism is idle, without imposing a burden on the pump-operating motor. Spool 83 is adjusted in bore 40 by an eccentric pin 9| supported for oscillation in the lower portion of the body 31, a shaft 92 projecting from the support for the eccentric pin to the exterior of the mechanism to effect the manipulation of the pin. By such rotation of the support, the spool 83 may be lowered from its centered position, wherein pump flow is discharged to reservoir 32 to the position shown in Fig. 6 which provides for automatic operation of the press and the feeding mechanism 23.

When the spool 83 is in the latter position and spool 52 also is in the position shown, pump fluid will be directed through the line 82 to a second control valve mechanism 93 which is attached to the rear end of a fluid motor 9 employed to drive the feeding mechanism. Fluid motor 94 may be of any suitable type, the one illustrated having an inlet port 95 and an outlet port 96. Valve 93 has a passage 91 which establishes direct communication between the line 82 and the motor inlet 95, thus, fluid supplied to line 82 will flow directly into the fluid motor to eifect the operation thereof. This fluid will be exhausted through the outlet port 96 into a passage 98 formed in valve 93. Passage 98 leads to the outlet port I00 01' the valve mechanism, 93,

operate '5 Q which outlet port connected by a line I-Itl with reservoir 8.2. 'As long as hold is permitted to to the fluid motor 94 and outwardly through the outlet passage 98, port Ito and line Illl to the reservoir, the fluid motor will operate. The rate vet-operation may be controlled through the adjustment of a bypass .valve It! which is disposed in a passage ice extending between the passages 91 and 9.8 in the valve .93. When the fluid motor--94 operates, due to the flow of fluid therethrough, the operating shaft 1 ea thereof will be rotated. This shaft projects from the fluid motor 94 and keyed at its outer end to a hub 4-8.5 journalled in bearings I 06. The hub has an eccentric portion m the purposes of which will appearas the description proceeds.

Theouter portion of the hub N is provided with an enlargement Its in which a dove-tail groove 409 is termed. This groove slidably re oeives va member I II! from which a crank pin II I ing rod H3, the opposite end of which is sun- .ilarly-connected to a pin H4 on a crank .arm I I 5; this crank arm is secured to a shaft H6 which is in turn keyed to the driver section I ll of a onc way clutch.

This clutch includes a driven section I it which is iormed with or suitably secured to a feed roll I20, the latter being journalled for rotation in a frame IZI Motion is transmitted from the driver section II! to the driven section Ht through the provision of spring-pressed balls I 22 disposed between angular surfaces I 2 3, formed on the driver, and the inner surface of the driven section H8. When-the driver section is revolved in the direction of the arrow in Fig. 3 the balls I22 will be wedged between the inclined surfaces I23 and the driven section locking the sections together for rotation in unison. Movement of the crank arm II5 to cause rotation of the section I'I'I in this direction is caused by rotation of the driving motor and the motion of the crank end I99 operated thereby. This movement takes place during one-half a revolution of the motor shaft. During the other half of such a revolution, the driver section II l is revolved in the opposite direction. Such movement will not be transmitted to the driven section and feed roll since the one-way clutch permits relative movement between these elements when the motion of the driving section is reversed.

The feed roll is positively prevented from backing up or overrunning by a brake I24 comprising ill) a lined band I25 which is connected at one end to the frame as at lzli'and at the opposite end to a spring-pressed block I21, this block being engaged by a rod I 28 which is secured to a split collar I30 surrounding the eccentric portion ID? of the hub N35. The eccentric I01 is so related to the crank pin III that the brake will be applied at the proper time to prevent overrun or reverse movement of the feed roll. The degree of rotation of the feed roll during each forward movement of the driver member is regulated by the adjustment of the member I ll] relative to the axis of rotation of the hub I05 I "In order that the stock being fed by the feeding mechanism will be frictionally held in contact the feed roll, there is provided a pressing roll I31 which is journalled in suitable bearings I32..carried by the frame I24. The presser roll I is resilientl urged toward the feed roll by coil sprin s I83 disposed between the upper sections :of the bearings I32 and adjusting screws I34- Through the adjustment of the screws I34, the force of the springs I 33 may be varied to cause more or less friction between the stock and the feed roll. A pair of guide rollers I35 are mounted for rotation about vertical axes on a transversely extending web of the frame at the inlet side :of the feed roll, to center the stool: betweenthe feed rolls, these guide rollers also tending to eliminate friction which might affect the feeding operation.

In the operation of the press and feeding mechautism, the press ram and feeding rolls are alternately operated, the-latter performing a feeding operation for each revolution of the driving motor fi l. To efiect the alternate operation of the ram and feed roll, the valve 93 is provided with a poppet I3?! disposed in the passage 98. This poppet is normally maintained in .an'open position by a. spring I38 in order that the fluid discharged from the flu-id motor may flow to exhaust without appreciable obstruction. .After the feed roll has advanced the stock toward the ram and the driving motor 94 exccutesa portion of the second half of the revolution, the poppet I3? is actuated to interrupt the flow of fluid to exhaust and direct the same through a second :outlet or con trol port I' lIl. To close poppet I 3?, the motor shaft Hi l is provided with a cam I lI which enages a roller I42 provided on the end of a plunger Hi3, this member being disposed for sliding movement the framework of the feeding mechanism. The outer end of the plunger I45 engages one arm Md of a bell crank M5 the second arm Hit of which engages one end of a push rod I47; this push rod in turn engages the outer end of a stem formed with poppet I 31 and projecting from the casing of the valve 93. A suitable compensating connection M8 forms a part of the push rod M! to absorb additional movement, after the poppet .is closed, and prevent injury to the machanisrn. After the poppet valve has been closed, fluid discharged from the fluid motor M will flow through line I 50 to groove 43 in valve body 37!. This groove communicates with groove 42 which in turn communicates through ports 54, with chamber 53 at the lower end of the shuttle valve to. Fluid thus introduced into the lower end of the chamber 53 will move the shuttle valve upwardly in opposition to the force of the spring until groove 6'! in the shuttle valve establishes communication between the inlet line 35 and the groove 46 through groove 45 and ports 58 and 59.

After shuttle valve 66 has been elevated the flow of exhaust .fiuid from motor 94 will be obstructed with the efifect of stalling the motor. Before this motor stalls, however, the volume of fluid necessary to elevate the shuttle valve exhausted by the motor is sufiicient to permit motor 94 to advance far enough to cause the high point on cam MI to pass follower I42. This action would normally permit poppet I37 to return to an open position but due to the pressure existing beneath the shuttle valve, in line I50 and passage 98 the poppet is retained in closed position.

Since groove 46 is connected by line I5! with the upper end of power cylinder 26, the placing of the shuttle valve in an elevated position will connect the source of fluid pressure with the upper end of the power cylinder. At this time 7. also, the lower end of the power cylinder will be in communication with the reservoir 32. This communication takes place through line I52. groove 43, ports 55 or 56 in the spool 52, ports II in the shuttle valve, chamber 12, passage I3, socket 65, ports 60, grooves 41 and 50, and line: 90. Flow of fluid along this path will be re-- stricted due to the reduced size of the passage I3 causing a back pressure to build up in the chamber 12, the lower end of the power cylinder and the passages connecting these members. This back pressure is transmitted to the lower end of the chamber 53 through passage '54 and serves to maintain the pressure previously introduced through line I50. The shuttle valve 66 will thus be retained in an elevated position and poppet I31 will be held closed during the downward movement of the ram. When movement in this direction is initiated, the arm 85 will move: away from the collar I8 permitting the shipper rod and valve spool 52 to move downwardly in response to the force of a spring I53 disposed in the valve casing 3'! between a washer I54 and a collar I55 surrounding rod I5, until ports 5? move out of registration with groove 44, at this time the path of fluid flow to the fluid motor 94 will be obstructed. Full pump volume will then be available for the operation of the ram and fluid motor 94 will remain idle until arm 8E] again engages collar 18 during the return movement of the ram, and moves valve spool 52 to reestablish communication between ports 51 and groove 44. When this communication is reestablished, the feeding mechanism will again be operated and the ram will remain stationary until another charge of fluid under pressure is supplied to the underside of the shuttle valve to initiate another operation of the ram.

Return or upward movement of the ram occurs after the ram has exerted the force determined by the setting of relief valve 34. When this valve operates to spill fluid directly from the pump 33 to reservoir 32 the ram ceases to move in a downward direction and the exhaust flow from the lower end of the power cylinder ceases. The back pressure is then dissipated through passages I3 and I4 and shuttle valve 66 is moved to its lowermost position by the force of spring 64. When the back pressure is dissipated, spring I38 moves valve I37 to an open position also and the mechanism is in condition for another cycle of operation which will occur as soon as the ram reaches a fully retracted position if the spool 83 is properly positioned as previously mentioned,

From Fig. 6 it will be noted that line I50 contains a restriction I56. This restriction serves to insure the retention of poppet I31 in closed position immediately after it has been closed by the push rod I4! even though the push rod is retracted due to the high point on cam I4I passing follower I42. Inasmuch as a poppet valve is used which poppet will readily open because of the relatively slight displacement of fluid, the use of the restriction in line I50 is desirable. This restriction is located in close relationship to port I40 and although it serves to obstruct fluid flow to retain poppet valve closed, such obstruction is insufficient to deleteriously affect the opening of the poppet valve when the ram stops moving downwardly and the shuttle valve drops.

The cam MI is provided with a relatively sharp projection to reduce the tendency of the device to stop with the poppet valve closed.

From the foregoing it will be apparent that a feeding mechanism has been provided which will operate to successively feed stock to a rain or other device for performing operations thereon. It will also be apparent that a hydraulic system has been provided for both the press and the feeding mechanism, which system provides for the alternate operation of the press ram and the feeding mechanism, each of these elements being retained in inactive condition during the active condition of the other. Due to this alternate operating arrangement no interference of one mechanism with the other can result.

I claim:

1. Mechanism for feeding elongated material to apparatus for performing operations thereon comprising a source of fluid pressure; a rotary fluid motor; a feed roll; motion transmitting means actuated by said fluid motor to rotate said feed roll a predetermined distance upon each cycle of operation of said motor, said means having a crank secured for operation by said motor; a one-way clutch for said feed roll having a driven member connected with said feed roll and a driving member; means for transmitting motion from said crank to the driving member of said clutch; a valve mechanism between said pressure source and said motor; and valve actuating means operated by and controlled in part by said fluid motor to govern fluid flow from said source to said motor to limit the latter to one cycle of operation at a time.

2. Strip feeding mechanism comprising a feed roll; a fluid motor; a source of fluid pressure; a pressure responsive valve for controlling the flow of fluid from said source to said motor; motiontransmitting means between said feed roll and motor having a crank connected for operation with said motor; a one-way clutch having a driven member secured to said feed roll and a driving member; a connecting rod between said crank and said driving member; means normally disposed to direct fluid discharged from said fluid motor to exhaust; and means actuated by said fluid motor for causing said last-named means to momentarily direct fluid discharged from said motor to said pressure responsive valve to cause the same to interrupt fluid flow to said fluid motor.

3. Strip feeding mechanism comprising a feed roll; a fluid motor; motion transmitting mechanism between said motor and feed roll, said mechanism having a crank operated by said motor; an oscillatory driver for said feed roll; a connecting rod transmitting motion from said crank to said oscillatory driver; clutch means connecting said oscillatory driver and feed roll when the former moves in one direction and disconnecting them when the driver moves in the opposite direction; brake means actuated by said motor to restrain said feed roll against rotation when said driver moves in said opposite direction; a source of fluid pressure; valve means between said pressure source and said fluid motor; and motion transmitting means actuated once during each revolution of said motor to operate said valve means to interrupt fluid flow from said source to said motor.

4. Strip feeding mechanism comprising a feed roll; a fluid motor; motion transmitting mechanism between said motor and feed roll, said mechanism having a crank operated by said motor; an oscillatory driver for said feed roll; a connecting rod between said crank and said oscillatory driver; clutch means connecting said oscillatory driver and feed roll when the former moves in one direction and disconnecting them when the driver moves in the opposite direction; brake means for said feed roll; eccentric means actuated by said motor to apply said brake means and restrain said feed roll against rotation when said driver moves in said opposite direction; a source of fluid pressure; valve means between said pressure source and said fluid motor; and motor operated cam and push rod means actuated once during each revolution of said motor to cause said valve means to interrupt fluid flow from said source to said motor.

5. Strip feeding mechanism, comprising a feed roll; a, fluid motor; motion transmitting mechanism between said motor and feed roll, said mechanism having a crank operated by said motor; means for varying the effective length of said crank; an oscillatory driver for said feed roll; a connecting rod transmitting motion from said crank. to said oscillatory driver; clutch means connecting said oscillatory driver and feed roll when the former moves in one direction and disconnecting them when the driver moves in the opposite direction; brake means actuated by said motor to restrain said feed roll against rotation when said driver moves in said opposite direction; a source of fluid pressure; valve means between said pressure source and said fluid motor; and motion transmitting means actuated once during each revolution of said motor to operate said valve means to interrupt fluid flow from said source to said motor.

6. In a mechanism for feeding strip material to apparatus for performing operations thereon having a fluid pressure operated member; feeding means for moving said strip material to said member to have the operations performed thereon; a source of fluid pressure; a fluid motor for driving said feeding means; control valve mechanism between said pressure source and said pressure operated member and between said source and said fluid motor, said control valve mechanism having an element responsive to fluid pressure to initiate the operation of said pressure operated member; a second element in said control valve mechanism responsive to the operation of said pressure operated member to govern fluid flow from said source to said fluid motor; flow directing means normally operative to direct the discharge from said fluid motor to exhaust; and means actuated by said fluid motor for causing said flow directing means to momentarily direct fluid discharge from said motor to said pressure responsive element to initiate an operation of said pressure operated member.

CECIL E. ADAMS.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 924,103 Von Philp June 8, 1909 1,740,844 Strout Dec. 24, 1929 1,782,362 McArthur Nov. 18, 1930 1,799,113 Miedbrodt Mar. 31, 1931 1,871,272 Jongedyk Aug. 9, 1932 2,006,040 Littel June 25, 1935 2,078,282 Sadgebury Apr. 27, 1937 2,080,292 Webber May 11, 1937 2,211,862 Rosenthal Aug. 20', 1940 2,222,168 Brooks Nov. 19, 1940 2,223,767 Lloyd Dec. 3, 1940 2,314,367 Pearson Mar. 23, 1943 2,320,659 Sahlin June 1, 1943 2,347,261 Harrington et a1. Apr. 25, 1944 2,379,668 Wacker July 3, 1945 2,413,638 McBlane Dec. 31, 1946 2,443,964 Sanders June 22, 1948 2,465,758 S-edgwick et a1 'Mar. 29, 1949

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