US3000359A - Hydraulic drive mechanism for moving an article to predetermined points - Google Patents

Hydraulic drive mechanism for moving an article to predetermined points Download PDF

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US3000359A
US3000359A US14229A US1422960A US3000359A US 3000359 A US3000359 A US 3000359A US 14229 A US14229 A US 14229A US 1422960 A US1422960 A US 1422960A US 3000359 A US3000359 A US 3000359A
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line
cylinder
fluid
bin
valve
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US14229A
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Gordon H May
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International Business Machines Corp
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International Business Machines Corp
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Priority to US14229A priority Critical patent/US3000359A/en
Priority to DEJ19564A priority patent/DE1232825B/de
Priority to GB9151/61A priority patent/GB915859A/en
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    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06K—GRAPHICAL DATA READING; PRESENTATION OF DATA; RECORD CARRIERS; HANDLING RECORD CARRIERS
    • G06K17/00—Methods or arrangements for effecting co-operative working between equipments covered by two or more of main groups G06K1/00 - G06K15/00, e.g. automatic card files incorporating conveying and reading operations
    • G06K17/0003—Automatic card files incorporating selecting, conveying and possibly reading and/or writing operations
    • G06K17/0012—Automatic card files incorporating selecting, conveying and possibly reading and/or writing operations with more than one selection steps, e.g. selection of a record carrier from a selected compartment of a compartmented storage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F15B11/12—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F15B11/12—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action
    • F15B11/121—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action providing distinct intermediate positions
    • F15B11/126—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action providing distinct intermediate positions by means of actuators of the standard type with special circuit controlling means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/02—Servomotor systems with programme control derived from a store or timing device; Control devices therefor

Definitions

  • HYDRAULIC DRIVE MECHANISM FOR MOVING AN ARTICLE TO PREDETERMINED POINTS Filed March 11, 1960 6 Sheets-Sheet 2 FIG. 2
  • FIG. 5 HYDRAULIC DRIVE MECHANISM FOR MOVING AN ARTICLE TO PREDETERMINED POINTS Filed March 11, 1960 6 Sheets-Sheet 5 FIG. 5
  • the present invention relates to hydraulic mechanisms for moving articles. More particularly the present invention relates to a hydraulic mechanism for rapidly moving relatively heavy articles very accurately to any one of a plurality of predetermined positions.
  • bins are divided into cells that are open at the top so that tags provided at the upper edges of the strips may readily be gripped and a selected strip thus be individually withdrawn from the bins by suitable strip drawing mechanism.
  • a plurality of bins is usually placed side by side to form a group or battery, and to withdraw a selected strip from the many adjacently positioned stacks of strips, the strip drawing mechanism may be arranged to move longitudinally across the row of adjacently positioned bins into position above the particular bin wherein the selected strip is stored while the bin in turn is moved in a direction transverse to the direction of movement of the strip drawing mechanism into a position wherein the cell containing the selected strip is located directly under said mechanism.
  • Another object of the invention is to provide a hydraulic drive mechanism by means of which any one of a number of adjacently positioned articles may selectively be moved along parallel paths into any one of a number of predetermined positions.
  • Yet another object of the invention is to provide a hydraulic mechanism for moving a plurality of bins individually into any one of a number of predetermined positions wherein many of the fluid conducting conduits and of the controls therefor are common to all the bins comprised in the arrangement.
  • Still another object of the invention is to provide a hydraulic drive mechanism for moving heavy articles, with means for arresting movement of the articles at preselected points, which means is controlled by the moving article itself.
  • FIGURE 1 is a fragmentary schematic perspective of a hydraulic system constructed in accordance with the invention for selectively moving any one of a plurality of adjacently positioned information storage bins;
  • FIGURE 2 is a schematic view of the hydraulic drive system as related to a single one of the information bins, illustrating said system in idle position;
  • FIGURE 3 is a schematic view similar to FIGURE 1, illustrating the system in a position wherein it moves the bin at a slow speed to a preselected position;
  • FIGURE 4 is a schematic view similar to FIGURES 1 and 2 illustrating the hydraulic system in a position wherein it moves the bin at a rapid speed to a preselected position;
  • FIGURE 5 is a timing diagram illustrating the manner in which the bin is set into motion and in which it is brought to a halt depending on whether it is moved at a slow speed or an accelerated speed;
  • FIGURE 6 is a fragmentary perspective of a hydraulically operated carriage and an information storage bin mounted thereon.
  • each of the bins 10 in a row of juxtaposed bins is supported upon a hydraulically operated slave cylinder 12 for movement therewith and each of said cylinders forms part of a carriage 14 which may comprise two axially spaced blocks 15a and 15b that are rigidly secured to the slave cylinder 12 near the opposite ends thereof and which slide upon a guide rail 16.
  • a piston head 18 Arranged within each slave cylinder 12 is (FIGURE 2) a piston head 18 that is held stationary in space by two piston rods 20a and 20b which project from the opposite end faces of the piston head, pass through the opposite end walls 22a and 22b of the slave cylinder 12 and are firmly mounted in stationary side structures 24a and 24b respectively, of the machine frame.
  • the bottom edge 39 of the other bar 30 is formed into an undulating cam surface and presents a sequence of alternate downwardly directed lobes 40 and upwardly receding recesses 42 to a cam follower roller 44 that may be transversely aligned with the detent 34 FIGURE 6), but is shown laterally displaced in FIG- URES 1-4 for clarity of illustration.
  • Said roller is pivotally supported at the upper end of a plunger 46 (FIG- URES 2-4 and 6) which is slidably received in a sta tionary pump cylinder 48 and is urged upwardly to hold the cam follower roller 44 in engagement with the camming edge 39, by suitable spring means indicated schematically at 50.
  • hydraulic fluid is supplied into its slave cylinder 12 on one or the other side of the piston 18 through the piston rods 20a and 20b which are of tubular construction and which are provided with circles of ports 52a and 52b, respectively, adjacent the piston head 18.
  • Said tubular piston rods are connected to conduits 54a and 54b, respectively, and all the conduits 54a and 54b comprised in the apparatus (FIGURE 1) branch off from two main lines 55a and 55b (FIGURES 1-4).
  • Each of said main lines may selectively be connected to a suitable source of hydraulic fluid marked by the arrows 56 which is held under relatively high pressure, such as 500 pounds per square inch, while its companion is connected to an escape or drain line 58 leading to a suitable sump (not shown), by appropriate setting of a direction control valve 60.
  • said valve is represented by a cylinder 62 within which is slidably received a control spool 64 comprising three axially spaced line blocking piston sections 64a, 64b and 64c and provided with a stem 66 that extends into, and may be actuated upon by a solenoid 68.
  • the control spool 64 is ordinarily held in the position shown in FIGURE 2 wherein line 55b is connected to the source of pressure fluid and line 55a is connected to the escape line 58. Under these conditions the escape line 58 would be connected to the left sides of all the slave cylinders comprised in the system and fluid under pressure would be directed to the right side of all the cylinders causing rightward movement of the slave cylinders relative to their stationary pistons 18, provided additional control valves to be presently described would permit unobstructed flow of hydraulic fluid through the lines 55b, 54b and 55a, 54a.
  • the main lines 55a and 55b each bifurcate into two parallel branches 55a, 55a" and 55b, 55b", respectively, over a stretch located intermediately of the direction control valve 60 and the runs of said main lines 55a and 55b from which the conduits 54a and 54b lead to opposite ends of the individual slave cylinders.
  • Flow of fluid through the main line branches 55a and 55b is controlled by a main flow control valve 70 having restricted passages therein, the valve being adjustable from a position wherein it blocks both said main line branches 55a and 55b (FIGURE 2) to a position wherein it unblocks both said branches (FIGURES 3 and 4).
  • the main line branches 55a" and 55b" are controlled by a booster valve 71 having unrestricted passages, the valve being normally held in a position wherein it blocks both said branches (FIGURES 2 and 3).
  • an individual operation conditioning mechanism 72 is associated with each of the cylinders (FIGURE 1) and is normally set to block both the conduits 54a and '54! leading from the main lines 55a and 55b to the interior of a selected cylinder through the tubular piston rods 20a and 20b thereof.
  • the operation conditioning mechanisms 72 may individually be actuated to unblock both said conduits irrespective of which is to serve as the pressure 'line and which as the escape line.
  • the mechanisms 72 serve the additional purpose of actuating individually the above mentioned detents 34 for the slave cylinders.
  • control spool 74 comprising three axially spaced piston segments 74a, 74b and 74c that are adapted to block the entrance and discharge ports of the cylinder 38.
  • a control spool 74 comprising three axially spaced piston segments 74a, 74b and 74c that are adapted to block the entrance and discharge ports of the cylinder 38.
  • Mounted upon the uppermost piston segment 74c and projecting upwardly therefrom is the hereinbefore mentioned rod 36 that forms the detent 34 at its upper end.
  • the conditioning mechanism 72 is held in the position 4 illustrated in FIGURE 2, by pressure fluid delivered into the cylinder 38 below its lowest piston segment 74a through a line 76 that may be connected to the common source of pressure fluid by an auxiliary control valve 78.
  • a segment 80a of a control spool 80 that is slidably received within a cylinder 82 is in a position wherein the line 76 is connected to the source of pressure fluid 56 while another piston segment 80b of said spool is in a position wherein it blocks a conduit 58 leading to the sump.
  • valve 78 In this position of valve 78, the pressure fluid is applied against the lowermost piston segment 7 4a of spool 74 over the total transverse area of the cylinder 38, and said spool is therefore held in the elevated position illustrated in FIGURE 2 in spite of the pressure exerted against the top surface of the uppermost segment 740 through a pressure line 84 because pressure supplied through line 84 bears only against the annual area of said uppermost segment 74c surrounding the detent rod 36.
  • valve 78 If it is desired, however, to move a particular bin, the spool of valve 78 is moved to the right, by energization of'a solenoid 86 into the position illustrated in both FIGURES 3 and 4, wherein the piston segment 80a blocks the pressure line 56 and the piston segment 8% unblocks the sump line 58. As a result thereof the fluid contained in the bottom of control cylinder 38 may escape to the sump in response to the pressure exerted upon its uppermost piston segment 740 through line 84 and the control spool 74 drops to the position illustrated in FIGURES 3 and 4.
  • fluid under pressure may enter one side of the slave cylinder while fluid may escape into the sump firom the opposite side of said slave cylinder (depending on which of the main lines 55a and 55b is connected to the source of pressure fluid and which is connected to the sump by the particular position of direction control valve 60 at the moment), whenever the main flow control valve 70 has been actuated to unblock the branches 55a and 55b of the main lines.
  • the detent 34 is withdrawn from whatever notch 32 of the rack bar 28 of the corresponding slave cylinder it engaged, and the particular slave cylinder may thus begin to move in one or the other direction depending upon the setting of the direction control valve 60.
  • the main flow control valve 70 is schematically represented as formed by a cylinder 88, the passages through which are of less cross-sectional area than the lines 55a and 55b.
  • a control spool 89 comprising three axially spaced piston segments 89a, 89b and 890.
  • the piston segments 89a and 8% block the main line branches 55a and 55b, respectively, when held in the elevated position illustrated in FIGURE 2, so that no pressure fluid can be delivered to any of the slave cylinders 12 nor any fluid escape from said cylinders.
  • the bottom of the cylinder 88 is connected to a line 90 that is ordinarily blocked by the segment 91a of a control spool 91 which is slidably received in the cylinder 92 of a control valve 94.
  • Both the line 90 and the bottom of cylinder 88 contain fluid which fills the cylinder to a level whereat it holds the control spool 89 in the elevated line-blocking position illustrated in FIGURE 2, but this fluid is under no more pressure (10-30 p.s.i.)
  • the spool 91 of the valve 94 is pulled to the left, as viewed in FIGURE 2, by energization of a suitable solenoid 96, into the position illustrated in FIGURES 3 and 4 wherein the piston segment 91a unblocks the line 90 and permits the fluid in cylinder 88 to flow under the force of spring 95 from the line 90 through a conduit 98 to an expansible fluid accumulator 100.
  • the resultant drop of the piston segments 89a and 89b unblocks the main line branches 55a and 55b so that high pressure fluid is applied to all the operation conditioning mechanisms 72 comprised in the system through one of said main line branches while the other main line branch is ready to conduct displaced fluid from any one of the slave cylinders into the sump as soon as the control valve 78 of any one of said cylinders is actuated.
  • solenoid 68 sets the direction control valve 60 to the position illustrated in FIGURE 3 wherein fluid under pressure is delivered into line 55a and line 55b is connected to the sump.
  • Energization of bin selection solenoid 86 sets the valve 78 to a position wherein the bottom of the detent actuating cylinder 38 is connected to the sump as likewise illustrated in FIGURE 3.
  • the detent 34 is withdrawn from the notched bar 28 of the slave cylinder, and the piston sections within said cylinder assume a position wherein the conduit 54a of the selected slave cylinder communicates with the main line 5511 (which is connected to the source of fluid under pressure at the moment), and the conduit 54b of the selected slave cylinder is connected to the main 5511 (which is connected to the sump).
  • the energized solenoid 96 places the control valve 94 into the position shown in FIGURE 3, wherein the escape line 90 at the bottom of cylinder 88 of the main flow control valve 70 is unblocked, so that fluid from the bottom of said cylinder may flow to the expansible accumulator 100 enabling the spring 95 at the top of the cylinder 88 to lower the piston segments 89a and 89b to the position illustrated in FIGURE 3 wherein both the main line branches 55a and 5512 are unblocked. Fluid under pressure may therefore reach the left side of the selected slave cylinder (but of none of the other cylinders) and any fluid in the right side of the selected slave cylinder (but in none of the other cylinders) may escape to the sump. With the detent 34 of the selected cylinder (but of no other slave cylinder) withdrawn, the selected slave cylinder, and only the selected slave cylinder, moves to the left relative to its stationary piston head 18, as fluid is forced into its left side.
  • means are provided that arrest the advance of the moving bin very accurately 6 at any one of a plurality of equi-spaced predetermined stations of its range of movement in response to de-energizatiou of the control solenoid 96 at a time when the moving bin has just passed the directly preceding station and before it has approached the selected station too closely.
  • the plunger 46 As the cam follower roller 44 on the plunger 46 associated with a slave cylinder in motion rides up and down the lobes and depressions of the camming bar that moves with the slave cylinder, the plunger 46 is reciprocated between a position wherein it is partially withdrawn from its cylinder 48 (FIGURE 3) and a position wherein it is fully inserted into said cylinder (FIGURE 4) and forces the fluid initially contained therein through the line 102 into the escape line 90 at the bottom of the main flow control cylinder 88.
  • control circuitry of an information storage machine efiects de-energization of the stop control solenoid 96 to arrest the advance of a moving bin at a predetermined station of its range of movement
  • said circuitry is arranged to efiect in quick succession the deenergization of the bin selection solenoid 86 which permits the bin selection valve 78 to return to the position illustrated in FIGURE 2 wherein the line 76 at the bottom of the bin control cylinder 38 is connected to the source of pressure fluid 56.
  • the electronic tCOtDIOl circuitry effects energization of the solenoid 86 of the bin selection valve 78 associated with the slave cylinder of the selected bin. This is effective to withdraw the detent 34 and thus releases the slave cylinder of the selected bin for operation. It is also effective to conmeet the conduits 54a and 54b of the selected cylinder to the main lines 55a and 55b, respectively, in the manner described hereinbefore.
  • the control circuitry also effects energization of the start and stop control solenoid 96 to set the valve 94 to a position wherein it connects the escape line 90 of the main flow control cylinder 88 to the expansible accumulator 100 which causes the piston sections 89a and 89b in said cylinder 88 to unblock the main line branches 55a and 55b (FIGURE 4).
  • the solenoid 68 of the direction control valve 66 remains de-energized and said valve, therefore, remains in a position, wherein it connects the source of pressure fluid to the main line 55b and opens the main line 55a for discharge into the sump as illustrated in FIGURE 4.
  • de-energization of the bin selection solenoid 86 allows fluid under pressure to enter the bin control cylinder 38 and lift the detent 34 into engagement with a notch 32 in the bar 28 of the operating slave cylinder while connecting the opposite ends of said slave cylinder for direct communication with each other to permit the slave cylinder to assume the exact position determined by full engagement of the detent 34 with the notch 32.
  • the pressure upon the hydraulic pressure fluid and the size of the conduits in the described system are so chosen that the selected slave cylinders advance with a predetermined speed which permits the bins to be brought to a halt Within a relatively short distance.
  • This speed of advance may be adequate :as long as the bins are to be moved over a relatively short distance to reach theirnew stations, but if they have to travel relatively large distances to reach their new stations, it may be desir able that they move at a greater speed over at least a part of their intended journey to reduce the time an operator has to wait before the information storage machine supplies the requested data.
  • the drive mechanism of the invention therefore comprises means for boosting the speed of movement of the slave cylinders whenever a'selected bin has to move over a distance exceeding a certain minimum number of consecutive stations, and it also comprises means for reducing the speed of the accelerated bin to a standard level an adequate distance in front of the new station to permit the hereinbefore described bin arresting arrangement to halt the moving bin at precisely the intended station.
  • main lines 55a and 55b are split into parallel branches 55a, 55a" and 55b, 55b over an intermediate portion of their length, and that the resultant pairs of coacting branch lines 55a, 55b and 55a, 5512 are controlled by separate valves 70 and 71, respectively, as described hereinbefore.
  • branch lines 55a, 55b are opened which is accomplished by actuation of the main flow control valve 70 in the manner described hereinbefore, but when a bin is to be moved over a relatively large distance the branch lines 55a", 55b" are opened in addition to the lines 55a and 55b by proper actuation of the booster valve 71 to increase the volumetric rate of fluid flow to the expanding side of the operating slave cylinder and to provide additional space for fluid to escape from the opposite side thereof.
  • the booster valve 71 is formed by a cylinder 106 having passages whose cross-sectional areas are equal to those at lines 55a" and 55b".
  • the cylinder is provided with an upper portion 107 of reduced diameter within which is slidably received a piston stem 108 that extends into the cylinder proper whereat it carries a control spool 110 comprising three axially spaced piston segments 110a, 110b, and 1100.
  • the two lower segments 110a and 11Gb are arranged to block the main line branches 55a" and 55b", respectively, when the spool 110 is in the elevated position illustrated in FIGURES 2 and 3 so that said branches do not partake in the operation of the system.
  • the lower end of the cylinder 106 is connected to the source of fluid under pressure by means of a line 112 which is controlled by a valve 114 that is normally set to connect said line 112 to the source of pressure fluid as in FIGURES 2 and 3, but which may be actuated by a solenoid 116 to connect the line 112 to the sump as shown in FIGURE 4.
  • the solenoid 116 When a selected bin is to be moved to a station that is removed from the station at which the bin is at rest by a distance extending over several intermediate stations, the solenoid 116 is energized and sets the control valve 114 to the position shown in FIGURE 4, wherein it blocks the supply of pressure fluid and connects theline 112 to the sump. With the fluid in the bottom of the cylinder 106 thus allowed to escape from the cylinder, pressure permanently applied to the top end of the piston stem 108 through a pressure line 118 connected to the upper end of the narrow cylinder portion 107 moves the piston rod to the position illustrated in FIGURE 4 wherein the auxiliary booster lines 55a" and 55b" are unblocked.
  • the booster valve 71 is opened to accelerate movement of a selected bin to a new station whenever the bin has to travel a distance extending over more than three consecutive stations to reach its new position.
  • the control solenoid 96 of the main flow control valve 70 and the control solenoid 116 of the booster valve 71 are energized simultaneously to set said valves to positions wherein they unblock the lines 55a, 55b and 55a", 55b" so that the bin may quickly reach a high speed of movement.
  • the booster valve 71 is closed at a point in advance of the intended new position of the bin by a distance that is adequate to allow the advancing bin to slow down to the speed level it would have reached, if the flow control valve 70 alone had been opened.
  • said main flow control valve 70 is closed in the customary manner by de-energization of the start and stop solenoid 96 at a point directly beyond the immediately preceding station and thus sufliciently in advance of the intended new position of the bin to permit the bin to slow down and be fully arrested at precisely its new place of location by the above described sequence of stop operations.
  • the abscissa X marks the increments of movement of a bin from a station I wherein it presents its first cell to the stripdrawing mechanism through station )ClI wherein it presents its last cell to said mechanism
  • the ordinate Y indicates the speed of movement of the bin as effected by operation of its slave cylinder 12.
  • the bin reaches the speed indicated by the level marked S in FIGURE 5, and if the bin is to stop at station II, the stop control solenoid 96 and the bin selection solenoid 86 are de-energized to initiate the stop operations as soon as the advancing bin reaches the point marked P i.e. when it has scarcely commenced to move.
  • the speed of the advancing bin continues to increase, however, since its camming bar 30 presents the receding edge of a depression 42 to the pump-operating cam follower roller 46 and no fluid is therefore forced into the blocked escape line 90 of the main flow control cylinder 88.
  • the solenoids 96 and 86 When the bin is to come to a halt at station III or station IV, the solenoids 96 and 86 must be de-energized at points P or P respectively, which are located in front of the intended destination of the bin by a distance almost as large as the distance between two consecutive stations of the bin, and at points T or T respectively, the cam-actuated pump 46/48 begins to force fluid through the line 90 into the main flow control cylinder 88 so that the speed of the bin decreases as indicated by the oblique lines 0 and O and the bin comes to a halt at precisely station III or station IV, as the case may be.
  • the bin is to move from station I to station V whereat it is to present its fifth cell to the strip-drawing device.
  • the control solenoids 96 and 116 are both energized simultaneously to open both the main flow control valve 70 and the booster valve 71, and pressure fluid will be delivered to the appropriate side of the cylinder of th selected bin through both the branches 55a, 55a", or 55b, 551), as the case may be, while adequate space is provided for fluid to escape from the opposite side of the cylinder at an accelerated rate.
  • the bin gains speed more rapidly and will rise to a higher level than was the case when the flow control valve 70 alone was opened.
  • both the solenoids 96 and 116 are energized to open the flow control valves 70 and 71 causing the bin to gain speed until it reaches points U to U respectively, which are located in front of the .intended destination by a distance about equal to the sum of the intervals between four consecutive stations.
  • the control solenoid 116 is de-energized to close the booster valve 71 causing the bin to slow down as indicated by the oblique lines Q; to Q in FIGURE 5, to the speed level S established by flow of pressure fluid through the main line branch 55a or 55b only.
  • closure of the main flow control valve 70 effected by de-energization of the start and stop solenoid 96 at points P to P a distance in front of the destination points VI to XII, respectively, will bring the moving bin to a halt at precisely the intended point of destination.
  • the pressure line 118 at the top of booster cylinder 106 has a restricted passage, as indicated at 120, which is by-passed by a shunt line 122 that contains a valve 24 which permits fluid to flow from the source of pressure fluid toward the cylinder 106 but blocks any flow of fluid in the opposite direction.
  • a shunt line 122 that contains a valve 24 which permits fluid to flow from the source of pressure fluid toward the cylinder 106 but blocks any flow of fluid in the opposite direction.
  • the described hydraulic system provides for individual movement of any one of a plurality of adjacently positioned bins to any one of a plurality of consecutive stations, and this movement may take place in either direction and at a relatively slow or a relatively high speed depending upon the distance which the bin has to travel from its initial position to its destination. It places the driven bin very accurately at its point of destination whether the bin is moved at a slow speed or a high speed.
  • the flow of the motion-effecting high pressure fluid to the operating slave cylinder is interrupted by camming means that travel with the bin, without need for said camming means to handle high loads which would quickly wear out both the camming means and the cam follower and thus seriously shorten the useful life span of the arrangement.
  • This is accomplished by actuating the main control valve for the high pressure line through a low pressure hydraulic systern which may be acted upon by the camming means without excessive wear.
  • the hydraulic drive arrangement of the invention is relatively simple and a large part of its conduits and control valves, i.e.
  • Arrangement for moving an object to predetermined points along a rectilinear path comprising: a slave cylinder drivingly connected to the object; high pressure fluid lines connected to the slave cylinder; a control valve connected across the fluid lines, the control valve being adjustable from an open to a closed position to regulate the fluid pressure applied to the slave cylinder and thus control movement of the object; and means for regulating the control valve, said means including a fluid accumulator, a valve means, a pump, a low pressure fluid line connecting in series the accumulator, valve means, pump and control valve, the valve means being adjustable to control fluid flow between the control valve and the accumulator, cam means movable with the object, the cam means being in operative engagement with the pump, and means operable to close the valve means and permit the pump to force fluid into the control valve to close the control valve and arrest movement of the object.
  • Arrangement for moving-an object to predetermined points along a rectilinear path comprising a slave cylinder arranged to support said object; high pressure lines leading into said slave cylinder; a control valve for said lines having line-blocking components settable from a first position wherein they connect one of said lines to a source of'fluid under high pressure and the other to a sump to effect operation of said slave cylinder and movement of said object, to a second position wherein they block said lines to arrest movement of the object; and means for actuating said valve including fluid in said valve to hold said line-blocking components thereof in line-closing position, a fluid accumulator, a low pressure line connecting said valve and said accumulator, lineblocking means settable from a position wherein it blocks said low pressure line to a position wherein it opens said low pressure line to permit escape of the fluid in said valve to said accumulator and thus cause the line-blocking components of said valve to open said high pressure lines, a pump connected to said low pressure line at a point between said valve
  • Arrangement for moving an object to predetermined points along a rectilinear path comprising a slave cylinder arranged to support said object; high pressure lines leading into said slave cylinder at opposite ends thereof; a control valve for said lines having line-blocking components settable from a first position wherein they connect one of said lines to a source of fluid under high pressure and the other of said lines to a sump to effect operation of said slave cylinder and movement of said object, to a second position wherein they block said lines to arrest movement of the object; and means for actuating said valve including fluid in said valve for holding said line-blocking components thereof in line-closing position, a fluid accumulator, a low pressure line connecting said valve and said accumulator, line-blocking means settable from a position wherein it blocks said low pressure line to maintain fluid in said valve and thus keep the lineblocking components of said valve in line-blocking condition to a position wherein it opens said low pressure line to permit escape of the fluid in said valve to said accumulator and thus cause the line-blocking
  • Arrangement for moving an object to predetermined points along a rectilinear path comprising a slave cylinder arranged to support said object; high pressure lines leading into said slave cylinder at opposite ends thereof; a control valve for said lines having line-blocking components settable from a first position wherein they connect one of said lines to a source of fluid under high pressure and the other of said lines to a sump to effect operation of said slave cylinder and movement of said object, to a second position wherein they block said lines to arrest movement of the object; and means for actuating said valve including fluid in said valve for holding said line-blocking components thereof in line-closing position, a fluid accumulator, a low pressure line connecting said valve and said accumulator, line-blocking means settable from a position wherein it blocks said low pressure line to maintain fluid in said valve and thus keep the line-blocking components of said valve in lineblocking condition to a position wherein it opens said low pressure line to permit escape of the fluid in said valve to said accumulator and thus cause the line-blocking
  • Arrangement according to claim 3 including a bypass line shunted across said low-pressure-linc-blocking means and provided with a valve permitting flow or" fluid from said accumulator to said low pressure line when said low-pressure-line-blocking means is in line-closing position, but blocking flow of fluid through said by-pass line from said low pressure lines to said accumulator.
  • Arrangement for selectively moving any one of a plurality of adjacently positioned objects to any one of a plurality of consecutive stations along parallel rectilinear paths comprising a plurality of adjacently positioned slave cylinders each arranged to move one of said objects, a notched positioning member and a camming member supported from each object for movement therewith, a pair of main lines selectively connectable to a source of fluid under high pressure and a sump, pairs of conduits leading from said main lines into opposite ends of said slave cylinders, an operation-conditioning mechanism adjacent each of said slave cylinders having detent means adapted to engage a notch in the notched positioning member of its respective object and settable from a cylinder-disabling position wherin it blocks the conduits leading from said main lines to its respective slave cylinder and projects said detent means into engagement with a notch in its coacting positioning member to an operation-conditioning position wherein its retracts said detent means from its co-operating positioning member and connects said conduits to said main lines, cylinder
  • Arrangement for selectively moving any one of a plurality of adjacently positioned objects to any one of a plurality of consecutive stations along parallel rectilinear paths with a relatively slow speed or a relatively fast speed comprising a plurality of adjacently positioned slave cylinders each arranged to move one of said objects in both directions; a notched positioning member and a camming member supported from each object for movement therewith; a pair of main lines; valve means settable between a position wherein it connects one of said main lines to a source of fluid under high pressure and the other one of said main lines to a sump and a position wherein it connects said first mentioned main line to a sump and said last mentioned main line to a source of fluid under high pressure to determine the direction of movement of whatever object is to be moved; pairs of conduits leading from said main lines into opposite ends of said slave cylinders; an operation-conditioning mechanism adjacent each of said slave cylinders having detent means adapted to engage a notch in the notched positioning member of its respective object, and settable

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  • Chemical & Material Sciences (AREA)
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  • Theoretical Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
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US14229A 1960-03-11 1960-03-11 Hydraulic drive mechanism for moving an article to predetermined points Expired - Lifetime US3000359A (en)

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Application Number Priority Date Filing Date Title
US14229A US3000359A (en) 1960-03-11 1960-03-11 Hydraulic drive mechanism for moving an article to predetermined points
DEJ19564A DE1232825B (de) 1960-03-11 1961-03-10 Hydraulische Antriebseinrichtung
GB9151/61A GB915859A (en) 1960-03-11 1961-03-13 Improvements in or relating to hydraulic positioning mechanisms

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1983001662A1 (en) * 1981-11-09 1983-05-11 Tadeusz Budzich Digital drive control of compensated valves
US4406423A (en) * 1980-04-28 1983-09-27 Wire Machinery Corporation Of America Reel support system
US4699042A (en) * 1985-02-23 1987-10-13 Kurt Stoll Fluid power actuator

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2821172A (en) * 1956-05-07 1958-01-28 C & D Lumber Co Power operated device for moving an element to selected positions
US2855752A (en) * 1955-10-21 1958-10-14 Brusque Rene Le Hydraulic device for controlling the feed and stop position of a machine element in cutting, sawing and slicing machines
US2860751A (en) * 1956-07-05 1958-11-18 Gen Electric Positioning device
US2922399A (en) * 1957-01-24 1960-01-26 Ibm Hydraulic drive and control therefor

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE925869C (de) * 1952-01-01 1955-03-31 Hans Doern Steuervorrichtung fuer mit Druckmittel betriebene Servomotoren zum Betaetigen maschineller Einrichtungen, z. B. fuer die Foerderkorbbeschickung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2855752A (en) * 1955-10-21 1958-10-14 Brusque Rene Le Hydraulic device for controlling the feed and stop position of a machine element in cutting, sawing and slicing machines
US2821172A (en) * 1956-05-07 1958-01-28 C & D Lumber Co Power operated device for moving an element to selected positions
US2860751A (en) * 1956-07-05 1958-11-18 Gen Electric Positioning device
US2922399A (en) * 1957-01-24 1960-01-26 Ibm Hydraulic drive and control therefor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4406423A (en) * 1980-04-28 1983-09-27 Wire Machinery Corporation Of America Reel support system
WO1983001662A1 (en) * 1981-11-09 1983-05-11 Tadeusz Budzich Digital drive control of compensated valves
US4699042A (en) * 1985-02-23 1987-10-13 Kurt Stoll Fluid power actuator

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Publication number Publication date
GB915859A (en) 1963-01-16
DE1232825B (de) 1967-01-19

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