Fluidic repeater

Abstract

A fluid repeater system may be balanced so that displacement of the load has a desired correspondence to displacement of the transmitter. This may be done by making the fluid resistance offerd to fluid flowing along a path from the source to the reservoir and through the feedback controlled directly by the load, exclusive of the resistance offered by such load feedback, approximately equal to that offered to fluid flowing along a path from the source to the reservoir and through the transmitter, exclusive of the resistance offered by such transmitter.

Description

BACKGROUND OF THE INVENTION

This invention pertains to fluidic, e.g. hydraulic or pneumatic, repeaters useful as remote indicators and servo proportional controllers for either amplication or remote operation, e.g. in seismic generators, aircraft controls, boat steering, automobile wheel tracking, plow jerkers, and vibration test equipment.

Hydraulic devices employing mechano-hydraulic transmitters including an obstructor moving relative to two liquid ports connected to a liquid supply having a drooping pressure-load characteristic are known. It is also known to employ as a receiver or responder a double acting piston moving in a cylinder whose ends are connected by fluid conduits to the transmitter liquid supply upstream of the transmitter ports and to connect the piston mechanically or hydraulically to an output. Various feedbacks from the output to the transmitter are also known.

SUMMARY OF THE INVENTION

According to the invention, means for feedback control, whether incorporated directly in the double acting piston or mechanically connected thereto, comprises variable cross-section surface passages, e.g. tapered grooves. These grooves may be in the ends of a double acting piston cooperating with ports or side recesses of a cylinder. The piston moves to variably throttle fluid vented from the high pressure ends of the piston ends of the piston to lower pressure portions of the system. The invention further includes improved transmitter, responder and receiver means useful with the feedback means of the invention, e.g. systems in which the transmitter has a single line output for actuating the responder or receiver, systems in which the transmitter operates by variable throttling, and systems employing rotary type transmitters and systems with rotary type feedback means. Other features of the invention and objects and advantages thereof will appear hereinafter.

The feedback venting and the transmitter venting flow passages are in parallel so that the rate of venting effected by the feedback means is dependent solely on the position of the feedback means.

Various applications of the invention, e.g. to crane control, seismic generator drive, swash plate angle control of a swash plate controlled motor-pump unit, four wheel drive, and master and slave systems are disclosed.

Furthermore, the double-acting piston may be a spool with lands at either end and acting about an internal annular flange extending from the surface of the cylinder to the surface of the hub portion of the piston spool. High pressure fluid ports, with pressure varied by the transmitter, are connected to axially-directed ports in the annular flange such that the pressure of the fluid in the conduits is directed against the inside wall of the respective piston land. The hub portion has variable cross section grooves that communicate with lower pressure portions of the system through a passage in the annular flange of the cylinder whereby the piston moves to variably throttle the fluid moving from the high-pressure conduits to the lower pressure portions.

Additionally, the transmitter includes an improved rotary transmitter that varies the pressure of the fluid in two conduits, but varies the pressure of the fluid in only one conduit at a time. Such an improved transmitter has numerous applications and can be used to control a swash plate pump/motor unit in such a way that as the pressure of the fluid in one conduit is varied, the motor rotates at varying speeds in a clockwise direction, and as the pressure of the fluid in the other conduit is varied, the motor rotates at varying speeds in a counterclockwise direction.

Also, the system may be balanced so that displacement of the load has a desired correspondence to displacement of the transmitter. This may be done by making the fluid resistance offered to fluid flowing along a path from the source to the reservoir and through the feedback controlled directly by the load, exclusive of the resistance offered by such load feedback, approximately equal to that offered to fluid flowing along a path from the source to the reservoir and through the transmitter, exclusive of the resistance offered by such transmitter.

BRIEF DESCRIPTION OF THE DRAWINGS

For a more detailed description of several preferred embodiments of the invention reference will now be made to the accompanying drawings wherein:

FIG. 1 is a largely schematic sectional view illustrating a fluidic repeater according to the referred embodiment of the invention;

FIGS. 2 and 3 are fragmentary views similar to FIG. 1 showing modifications;

FIGS. 4 and 5 are views similar to FIGS. 1-3 showing two further modifications;

FIGS. 6, 7, and 8 are elevational, sectional and end views respectively of the end of the amplifier piston of the FIG. 5 embodiment;

FIG. 9 is a view similar to FIG. 8 showing another embodiment;

FIG. 10 is a cross-sectional schematic view of a mechanical to fluidic translator according to the invention;

FIG. 11 is a sectional view of part of the spool valve shown in FIG. 10;

FIGS. 12, 13 and 14 are largely schematic sectional views showing further embodiments of the invention; and

FIGS. 15 and 16 are sectional views of feedback elements of the embodiments shown in FIGS. 12 through 14;

FIG. 17 is a largely schematic cross-sectional view illustrating a fluidic repeater according to an embodiment of the invention;

FIG. 18 is a view similar to FIG. 17 showing another embodiment;

FIG. 19 is a view similar to FIG. 18 showing an embodiment of the invention using only a single pressure line for control;

FIGS. 20 and 21 are views similar to FIG. 19 showing other embodiments of the invention using single control lines;

FIG. 22 is a sectional view of elements of the embodiments shown in FIGS. 20 and 21;

FIG. 23 is a fragmentary schematic sectional view of a portion of an embodiment of the invention;

FIG. 24 is a view similar to FIG. 23 showing a portion of another embodiment;

FIG. 25 is a fragmentary, largely schematic sectional view showing a portion of an embodiment of the invention;

FIG. 26 is a fragmentary sectional view of a commercial embodiment of the invention;

FIG. 27 is an elevational view of a section of FIG. 26 taken along lines 27--27;

FIGS. 28 and 29 are sectional views of valves used in the invention's embodiment depicted in FIG. 26;

FIG. 30 is a partially sectional view of another commercial embodiment of the invention;

FIG. 31 is a sectional view of the transmitter illustrated in FIG. 30 taken along lines 31--31.

FIG. 32 is a largley schematic sectional view illustrating another embodiment of the invention somewhat similar to the embodiment of FIG. 19;

FIG. 33 is a view similar to that of FIG. 32 showing a further modification;

FIG. 34 is a view largely in section showing a commercial embodiment and slight modification of the apparatus shown in FIG. 32;

FIG. 35 is a largely schematic sectional view illustrating a modification of the invention shown in FIG. 20;

FIG. 36 is a largely schematic view partly in section illustrating a modification of a form of the invention shown in FIG. 5;

FIG. 37 is a side elevation, largely in section, of a load cylinder with a feedback means incorporated therein in accordance with one form of the invention;

FIG. 38 is a side elevation, partly schematic, showing the invention incorporated in apparatus for loading a floating vessel by a crane located on a pier;

FIG. 39 is a largely schematic elevation, partly in section, of the hydraulic system and related parts of the apparatus shown in FIG. 38;

FIG. 40 is a sectional view of apparatus according to the invention incorporated into a system for varying the angle of a swash plate controlled motor-pump unit;

FIG. 41 is a view similar to FIG. 4 showing a modification;

FIG. 42 is an elevation, partly in section, showing apparatus incorporating the invention forming part of a seismic generator;

FIG. 43 is a schematic plan view of apparatus according to the invention employed for driving a four wheel drive vehicle;

FIG. 44 is a largely sectional view of apparatus according to the in-ention suitable for dual parallel, control, e.g. as in FIG. 43;

FIG. 45 is a largely sectional view of apparatus according to the invention for dual control of the master and slave type;

FIG. 46 is a partly sectional view illustrating another form of apparatus according to the invention;

FIG. 47 is a sectional view of an amplifier forming part of a system according to the invention;

FIG. 48 is a sectional view showing a modification of the amplifier of FIG. 47;

FIG. 49 is an elevation showing a dual rotary transmitter in accordance with the invention;

FIGS. 50, 51 are sections taken on planes 50--50 and 51--51 of FIG. 49;

FIG. 52 is a largely schematic view illustrating a rotary transmitter for venting a two-line system one line at a time with a single control lever;

FIG. 52A is a sectional view of the transmitter of FIG. 52 taken along lines 52A and connected to a responder;

FIG. 53 is a largely schematic sectional view illustrating a rotary transmitter for venting a two-line system one line at a time with a single control lever and a switching valve and a modified responder piston and cylinder;

FIG. 53A is a sectional view of an alternative embodiment of the responder of FIG. 53;

FIG. 53B is an end view of the cam pin of FIG. 53A;

FIG. 53C is a view similar to FIG. 53 showing how the transmitter of FIG. 52A is to be substituted for that of FIG. 53;

FIG. 54 is a largely schematic sectional view illustrating a rotary transmitter for venting two-line systems, each system vented one line at a time by two control levers, and switching a modified responder piston and cylinder;

FIG. 55 is a schematic plan view of a four-wheel vehicle wherein the wheels may be selectively driven individually or in unison.

FIG. 56 is a largely schematic sectional view showing a venting two-line system incorporating the equal length path embodiment of the balanced path concept;

FIG. 57 is a fragmentary view similar to FIG. 56 showing an alternative form of the equal length path embodiment of the balanced path concept;

FIG. 58 is a fragmentary view similar to FIG. 56 showing the balanced cross section embodiment of the balanced path concept;

FIG. 59 is a partial view of the responder of the system of FIG. 53 showing an alternative form of restriction for the outlet conduit;

FIG. 60 is a partial view of the responder of the system of FIG. 59 showing a further alternative form of restriction for the outlet conduit;

FIG. 61 is a largely schematic sectional view showing a venting two-line system incorporating the line restrictor embodiment of the balanced line concept;

FIG. 62 is a largely schematic sectional view illustrating the connection of a variable restrictor path-balancing unit to the responder of FIG. 56;

FIG. 63 shows the system illustrated in FIG. 21 as modified by FIGS. 22 and 24 and incorporating the line restrictor embodiment of the balanced paths concept;

FIG. 64 is a largely schematic sectional view illustrating a system having two-lines, one vented by the transmitter and one vented by the feedback, and incorporating the line restrictor embodiment of the balanced paths concept;

FIGS. 64A and 64B are partial views of the FIG. 64 system showing alternative forms of line restrictor; and

FIG. 65 is a largely schematic sectional view of two-line system wherein the transmitter vents one line and the amplifier feedback vents both lines and incorporating the line restrictor embodiment of the balanced paths concept.

DESCRIPTION OF PREFERRED EMBODIMENTS

Referring now to FIG. 1, a fluidic repeater comprises a pump or source (not shown) of fluid under pressure connected to conduits marked P and a sump or low pressure fluid reservoir (not shown) connected to conduits marked R. Usually the system will be hydraulic and use a liquid, e.g. mineral oil, as working fluid, but the following description refers to all embodiments of the invention and is also applicable to pneumatic systems wherein a gas, e.g. air, is the system fluid.

Fluid from pressure source conduit 11 flows through passages 13, 15 in transmitter body 17, through restrictions or orifices 19, 21 to passages 23, 25, and thence out through ports 27, 29. The ports empty into the interior of cylinder 31 formed in transmitter body 17. Cylinder 31 is vented to reservoir 51 by three ports 33, 35, and 37. A four landed spool 39 is moved axially back and forth in cylinder 31 by electromagnetic solenoid 41, which may also be a short stroke torque motor. The solenoid is biased to its midposition, as shown, by springs 40 and 42. When spool 39 is biased to mid position, as shown in FIG. L, lands 43 and 45 fully or substantially block ports 27 and 29. This reduces the transmitter's idle power requirements. In a modulating system both ports will be partially open in the mid-position of the spool.

Operationally, electric signals applied to solenoid or electric motor 41 moves spool 39 toward one end of cylinder 31. This opens either port 27 or 29 an amount whose magnitude is dependent upon the spool's movement. In a modulating system, the port not opened will be closed an amount also dependent upon the spool's axial movement. As one port is opened, e.g. port 27, pressure in passage 23 drops due to the increased fluid flow from the source through the flow restrictor or orifice 19, while closure of the other port, e.g. port 29, will cause a pressure rise in passage 25 due to the reduced flow through orifice 21. Flow passage 13 with orifice 19 and the flow passage 15 with orifice 21 thus provide fluid supplies of drooping pressure-load characteristics. Connected to this supply are ports 27, 29, and spool 39 with lands 43, 45. These provide a variable obstructor for opening and closing the ports this variably venting the fluid supplies to provide variable pressure outputs that vary in accordance with the obstructor's position. Since obstructor position is controlled by an electric motor, the system thus far detailed provides an electrofluidic transducer transmitter.

To prevent hydraulic locking of spool 39 because of the inherent slight leakage past lands 43, and 45, the spools are relieved by providing annular spaces 47 and 49 beyond lands 43 and 45 that communicate with ports 33 and 37. These ports lead to conduit 51 that is connected to reservoir 51. Spool 39 is provided with additional guidance by providing it with end lands 53 and 55. The ends of cylinder 31 are connected by fluid passage 57 that leads to chamber 58. Chamber 58 contains motor 51 and is vented to the atmosphere by passage 59.

The transmitter's varying fluid pressure outputs are conducted by fluid passages 61 and 63 to an amplifier comprising cylinder 65 formed in transmitter body 17. A double acting free piston 67 floats in cylinder 65, being free to move axially in response to pressure differentials at its ends 69, 71. Fluid passages 61 63 from the transmitter are connected to the ends of cylinder 65 so their pressures can act on the free piston's ends. The outer periphery of the piston is relieved by annular grooves 73 and 75, leaving lands 77 and 79 at the ends of the piston. Annular spaces 81 and 83 formed by grooves 73 and 75 are vented to the reservoir by fluid passages 85, 87. Lands 77 and 79 are provided with sloping grooves 89 and 91, respectively, whose depth decreases progressing from the ends of the piston toward grooves 73 and 75. Sloping grooves 89 and 91 vent pressure fluid from passages 61 and 63 past lands 77 and 79 to recesses 93 and 95 in the cylinders' sides and hence to the reservoir through passages 85 and 87. Suitable means, not shown, such as a key and slot, are provided to maintain grooves 89 and 91 in azimuthal alignment with recesses 93 and 95. The size of vent openings 97 and 99 connecting grooves 89 and 91 with recesses 93 and 95 increase and decrease when piston 67 is moved axially. This venting causes negative feedback to fluid passages 61 and 63. Higher pressure at one of passage 61 or 63 than at the other moves free piston 67 in the correct direction to increasingly vent these higher pressure to a reservoir through either groove 89 or 91. Relatively lower pressure in passage 61 or 33 than in the other moves free piston 67 in a direction to reduce venting of such lower pressure to the reservoir. Due to this variable negative feedback, piston 67 moves proportionally in response to the degree of movement of spool 39 and then comes to rest.

Free piston 67 could be connected mechanically to a suitable output such as an indicator, valve or other load. Cylinder 65 and piston 67 would then constitute parts of a receiver connected to the previously described transmitter. Passages 61 and 63 could be replaced by hoses, pipes, or other extended fluid conduits. The system would then constitute a remote indicating or proportional control system.

As shown in FIG. 1, however, piston 67 and cylinder 65 form parts of a fluidic amplifier. Piston 67 is relieved at its mid portion by annular groove 101. Annular space 103 formed by groove 101 is connected by fluid passage 105 leading to a source of fluid pressure. Lands 107 and 108 between groove 101 and grooves 73 and 75, cover outlet ports 109 and 110 in cylinder 65 when piston 69 is in mid position, as shown. When piston 69 moves axially toward one end of cylinder 65 in response to electric signals supplied to conductors 111 of motor 41, then ports 107 and 109 are uncovered in proportion to the piston's movement. One fluid conduit (hoses) 113 or 115 is thus connected to a source of pressure fluid through space 103 and passage 105 while the other of conduits is connected to reservoir through either space 81 and passage 85 or space 83 and passage 87. Hoses 113 and 115 are connected to opposite ends of load cylinder 117, which, together with piston 119 therein, forms a remote receiver.

When hose 113 or 115 is connected to the source of pressure fluid and the other to the reservoir, piston 119 moves in the direction of the flow from high pressure to low pressure. Piston rods 121, 123 extend through opposite ends of the cylinder 117, leaving equal areas of piston 119 exposed to pressures in cylinder 117. Piston rod 123 is extended to connect to a mechanical load, e.g. a valve, not shown.

Piston rod 123 is also connected mechanically by bar 125 to stem 127 of feedback valve 128. For easier viewing, valve 128 is drawn to a larger scale than load cylinder 117, but it is to be understood that the areas exposed to fluid pressure in the feedback valve are negligibly small compared to those of load cylinder 117.

Stem 127 extends through sealed opening 129 into cylinder cavity 131 of valve body 163 and connects to cylindrical valve closure 133. Closure 133 is provided with two sloping grooves 135 and 137 of increasing depth progressing axially from the ends toward the midportion of the closure. The deepest portions of the grooves being continued axially at constant depth for a certain extent as shown at 139 and 141. When the closure 133 is in midposition, as shown in FIG. 1, sloping portions of grooves 135 and 137 are in register axially with annular recesses 143 and 145 in the sides of cylindrical cavity 131. Recesses 143 and 145 communicate with ports 147 and 149, respectively, which, in turn, are connected to fluid conduits (hoses) 151 and 153. Conduits 151 and 153 are connected to ports 155 and 157, respectively, leading to the ends of amplifier cylinder 65.

The ends if cylindrical valve body cavity 131 are enlarged at 159 and 161 providing annular spaces communicating both with grooves 135 and 137 and also with passages 163 and 165 leading to conduit 167 connecting with the reservoir. When closure 133 moves axially, openings 169 and 171 between grooves 135 and 137 and the sides of cylindrical valve body cavity 131 are opened or closed in proportion to the degree of axial movement. This increases the venting to the reservoir of one of the feedback conduits 151 and decreasing the venting of the other.

Operationally, when a pressure differential across the ends of amplifier piston 67 causes the piston to move right or left, then load piston 119 moves in the opposite direction carrying with it attached feedback valve closure 133. This creates a pressure differential between conduits 151 and 153 opposite to that across piston 67. The feedback from cylinder 128 is therefore negative and tends to cancel out the pressure differential caused by movement of spool 39. This cancellation causes piston 67 to return to neutral or midposition. This discontinues the pressure differential across load piston 119, which then comes to rest in a displaced position proportional to the displacement of spool 39 that in turn was proportional to the signal strength applied to motor 41 at input 111.

Although motions of the various parts; e.g. transmitter spool 39, amplifier piston 101, load piston 119, and feedback valve closure 133; have been said to be proportional to the signal applied to the input 111 of motor 41, this is to be understood to mean only that there is a direct function between signal amplitudes and mechanical positions with an increase in signal strength causing an increase in mechanical travel. However, by appropriately shaping grooves 89, 91, 135 and 137, the proportionality may be made to approach closely a linear function. Other groove shapes than the simple sloping grooves 89, 91, 135 and 137 may be employed.

Referring now to FIGS. 2 and 3 there are shown modifications of the FIG. 1 construction. FIGS. 2 and 3 show only a portion of the apparatus shown in FIG. 1; the remainder of FIGS. 2; and 3's apparatus being the same as that of FIGS. 1 and 17. Parts that are the same as those in FIG. 1 are given like reference numbers and their description will not be repeated. An examination of FIGS. 2 and 3 will reveal that in FIG. 2 as in FIG. 1 lands 43 and 45 are disposed so as to substantially block ports 27 and 29 when spool 39 is in midposition; whereas in FIG. 3 lands 43 and 45 are disposed to leave both ports 27 and 29 partly open when spool 39 is in midposition. In other respects FIGS. 2 and 3 are the same.

FIGS. 2 and 3 differ from the FIG. 1 construction in two respects. First, guide lands 53 and 55 are omitted from spool 39, as are leakage return ports 33 and 37 and atmosphere vent passages 57 and 59. These of course can be used wherever it is found necessary or desirable. Secondly, and most important, in FIGS. 2 and 3 separate feedback valve 128 is omitted. Instead feedback valve means comprising grooves 135 and 137 controlling fluid conduits 151 and, respectively, 153 are provided directly on the ends of valve stems 121 and 123.

Referring now to FIG. 4 there is shown another modification of the FIG. 1 system. Again like parts are given like reference numbers and will not again be described.

The primary difference between the embodiments of the invention shown in FIGS. 1 and 4 is that in FIG. 4 the spool controlled ports 27 and 29 of FIG. 1 are replaced by nozzles 27A and 29A whose flow is controlled by obstructor 39A. The latter is a hand operated wheel, as distinguished from the electric motor actuated spool 39 of FIG. 1. Bearing 201 at one side of cylindrical obstructor 39A is internally threaded to receive threaded pin 203 on which the obstructor pivots. As the obstructor is rotated it moves axially approaching one or the other of nozzles 27A or 29A and moving farther away from the nozzle not approached. By this means the fluid pressure in conduits 23 and 25 is varied. Obstructor 39A is provided with unthreaded pivot pin 205 received in bearing 207 in obstructor support body 209. Nozzles 27A and 27B discharge into the interior of body 209. Radial passages 211 and 213 in pins 203 and 205, respectively communicate with the interior of body 209 and connect with axial fluid passage 207 which discharges into return line 35 leading to the fluid reservoir.

Another difference between the construction of FIGS. 1 and 4 lies in the construction of the feedback valve 128A that is mechanically linked to load piston rod 123.

Feedback valve 128A variably vents fluid passages 61 and 63 via grooves 135 and 137, which, in this case, are connected together to form one long groove. Venting through grooves 135 and 137 can also be outwardly into the spaces 220 inside annular sealing boots 221 and thence through groove 222 back to the reservoir. When feedback valve 128A has moved far enough to equalize the pressure in fluid passages 61 and 63, piston 101 moves back to neutral position. Load piston 119 remains in its new position as controlled by the setting of manual obstructor 39A.

Another difference between the embodiments of FIGS. 1 and 4 lies in the fact that in the FIG. 4 construction the amplifier piston 101 is not provided with feedback grooves in its ends like the grooves 89 and 91 of the FIG. 1 embodiment.

Referring now to FIG. 5 there is shown a further embodiment similar to the embodiments of FIGS. 1-4 wherein like reference numbers refer to like parts that will not be redescribed. As in the FIG. 4 construction, the FIG. 5 embodiment includes a manually actuated hand wheel type obstructor 39A cooperating with nozzles 27A and 29A, rather than an electric motor actuated spool 39 cooperating with ports 27 and 29 as in FIGS. 1-3. However, as in FIGS. 1-3, the amplifier piston is provided with feedback means. In the FIG. 5 construction instead of providing the ends of amplifier piston 101 with sloping grooves as at 89, 91 extending all the way to the outer ends of the piston as in FIGS. 1-3, the sloping grooves 89A and 91A of the FIG. 5 construction terminate where they run into and communicate with annular grooves 89B and 91B around the lands 77 and 79 respectively. Grooves 89B and 91B in turn communicate with the piston's ends via radial and axial flow passages 89C, 89D and 91C, 91D. Shape of grooves 89A and 91A is shown more clearly in larger scale detail views of FIGS. 6, 7 and 8. Short grooves 89A and 91A cooperate with annular grooves 89B and 91B to provide non-linear feedback correlative to the non-linear input of nozzle obstructor 39A. This effects a more nearly linear proportionality between hand wheel movement and amplifier piston movement.

FIG. 9 shows feedback groove 91E of rectangular cross section as an alternative to the V-shape cross section of groove 91A of FIG. 8.

No load cylinder and piston are shown in the FIG. 5 construction, but it is to be understood that amplifier output passages 113 and 115 connect via passages 117A and 117B leading to a suitable load cylinder which usually will be provided with further feedback means as in FIGS. 1-4. Without a load feedback the load piston will ultimately move to the limit of its travel regardless of the magnitude of the input at obstructor 39. The rate of this movement of the load piston will vary in proportion to the magnitude of the input at obstructor 39A. In some applications the load feedback means of the FIGS. 1-4 embodiments could also be omitted.

FIG. 5 illustrates the use of a filter screen 225 between conduit 11 leading to the source of pressure fluid and the orifices 19 and 21. This is desirable to prevent blockage of the orifices by foreign matter. This constructional detail, though not shown in FIGS. 1-4, it is to be understood as being applicable to all embodiments of the invention.

FIG. 10 shows an embodiment of the invention that is much the same as that of FIG. 5. Differences include modification of the feedback groove system in the amplifier piston and the use of an electric "flapper" in place of hand wheel obstructor 39A. Like parts are given like reference numbers and their description will not be repeated.

The amplifier piston feedback groove system in FIG. 10 is similar to the system illustrated by FIG. 5 except short sloping grooves 89A and 91A are omitted. An initial axial motion of the piston 101 sufficient to communicate annular groove 89B or 91B with vent passage 85 or 87 is required before any feedback will occur. Thereafter, further movement of the piston 101 in the same direction will cause increasing venting.

If desired, lands 77 and 79 can be inwardly flaring or tapered, e.g. conically or in other manner annularly relieved between annular grooves 73 and 89B along end and between annular grooves 75 and 91B at the other end, as shown in FIG. 11. This will effect a result similar to that attained by the embodiment illustrated in FIG. 5. The outermost parts of the lands will be cylindrical, for guide purposes, as shown at 79B.

Electric flapper 41A shown in FIG. 10 driving flapper type obstructor 39B includes horseshoe magnets 231 and 233 disposed opposite pole to opposite pole with flapper 39B pivoted therebetween at 235. Tension springs 237 and 239 connected to one end of the flapper and to motor housing 241 and adjustment screw 243 normally centers the other end of the flapper between nozzles 27A and 29A. When an electric signal is applied to either input 111A or 111B of solenoid 41A or 41B the flapper is magnetized a proportional amount. This moves it toward or away from nozzle 27A or 29A. This variably vents passages 23 and 25. Fluid leaving nozzles 27A and 29A returns to the fluid reservoir through passages 35A and 35B.

FIGS. 12-14 show rudimentary fluidic repeater apparatus according to an embodiment of the invention in which transmitter obstructor 39C or 39D is of the needle valve type rather than the spool valve type shown in FIGS. 1-3 or the jet interference types shown in FIGS. 4, 5 and 10. In FIG. 12 obstructor 39C is a cylindrical plug axially movable relative to cylindrical ports 27B and 29B. Plug 39C is provided with sloping grooves 251 and 253 similar to grooves 89 and 91 of the amplifier piston of FIG. 1. According to the axial position of plug 39C more or less fluid is vented from fluid source passages 23 and 25 to chamber 255 and then through passage 35 to reservoir return conduit 51. No means for moving plug 39C is shown, but it is to be understood that any suitable means can be used, e.g. any of the manual or motor means used in the previously described embodiments.

The transmitter obstructor shown in FIG. 13 is the same as that in FIG. 12. The transmitter obstructor shown in FIG. 14 is the same as in FIGS. 12 and 13 except that the ends of the obstructor plug 39D are provided with spiral helical grooves 251A, 253A spiraling inward and progressing axially towards the plug ends, rather than the sloping grooves 251, 253 of the embodiments of FIGS. 12 and 13. The two groove constructions are further illustrated in FIGS. 15 and 16.

Referring once more to FIG. 12, receiver piston 101C is provided with sloping feedback grooves 89 and 91 similar to those shown in the embodiments of FIGS. 1-3 whereby axial motion of piston 101C due to difference in pressure between fluid passages 61 and 63 causes such venting through chamber 255 and passage 35 to reservoir return conduit 51 as to eliminate the pressure differential. The receiver piston constructions of FIGS. 13 and 14 are the same as that of FIG. 12 except that instead of sloping grooves 89 and 91 of configuration like transmitter grooves 251 and 253, the receiver pistons of FIGS. 13 and 14 are provided with spiral helical grooves of configuration similar to the grooves 251A and 253A.

No applification is effected between transmitter plugs 39C and 39D and receiver pistons 101C and 101D. No load is shown connected to pistons 101C or 101D, but it is to be understood that they can be connected fluidically to load cylinders and pistons as are the amplifier pistons in the other embodiments, or mechanically, the same as feedback piston 133 in FIG. 1, for example, or pistons 101C and 101D could be connected to indicator or display means of minimum load power requirements.

The various vent groove configurations described herein as applicable to the transmitter plug (FIGS. 15 and 16), the amplifier or receiver piston (FIGS. 1-3, 5-14) and the load feedback piston (FIGS. 1-4) may be interchanged between the various embodiments described hereinabove or hereinafter, as may be desired or required for any reason, for example to correlate the transmitter obstructor position-vent function, the amplifier piston position-vent function, and the load feedback valve position-vent function.

Comparing the several embodiments of the invention thus far described it will be seen that operationally in each case a transmitter obstructor moves relative to a pair of openings. These may be side ports in a spool valve as in FIG. 1, jet nozzles as in FIGS. 4 and 10, or needle valve ports as in FIGS. 12-14. The obstructor and opening provide means to variably vent a pair of pressure fluid passages downstream from flow restrictors. Responder means, e.g. amplifier and/or load cylinders, are connected to the fluid passages. Feedback means from the amplifier and/or load cylinder variably vent the pair of fluid passages opposite to the variation by the obstructor. The feedback means comprises variable cross section surface passages in the amplifier or load or receiver piston or several of these or in the walls of the cylinders surrounding these pistons.

The responder means of the invention can be actuated by other forms of transmitter than those described above in which the transmitter variably vents a pair of fluid passages downstream from flow restrictors therein, the fluid passages upstream from the restrictors leading to a source of constant fluid pressure, and the pressures downstream from the restrictors being conducted by two fluid lines to the responder. Instead of variable venting, variable pressures can be generated by making the restrictors variable and conducting the downstream pressures by two lines to the responder. Furthermore, the transmitter may be modified to affect change in only one pressure. A single line may then be used between transmitter and responder. These various modifications will be described next.

Referring now to FIG. 17 there is shown an embodiment to the invention, the same as that of FIG. 2 insofar as the amplifier and receiver are concerned, but employing a modified form of transmitter. Like parts are given like reference numbers. In this embodiment, motor 41 acts to move spool 39 axially in cylinder 31 to vary the position of lands 43 and 45 relative to ports 27 and 29, as in FIGS. 2 and 3. However, conduit 11A connected to cylinder 31 leads to a pressure source rather than to a reservoir. The pressure in lines 61 and 63 leading to amplifier piston 101 are varied in accordance with the degree of throttling, or obstruction, produced by spool 39. Thus this is an example of control by variable obstruction of a pressure source. There is always a sufficient flow from lines 61 and 63 to the return reservoir conduit, for example 85, 89, and 167, to prevent the pressure in lines 61 and 63 from building up to supply pressure despite the throttling effect of spool 39.

The operation of the embodiment illustrated in FIG. 17 is the same as that of the embodiment illustrated by FIG. 1, in that electric signals inputted through electric motor 41 moves spool 39 to vary the pressure in lines 61 and 63. This differential pressure in turn moves amplifier piston 101, causing ports 109 and 110 to be opened to the reservoir and pump pressure, respectively. The differential pressure thus applied to load piston 105 causes it to move axially, moving connected clevis 124 to actuate a load (not shown). Negative feedback, in accordance with the preferred embodiment of the invention, is effected by grooves 89 and 91 in the amplifier and by grooves 135 and 137 in the load piston. The feedback provided by these grooves limits the travel of both the amplifier and load pistons so the load pistons movement varies in an amount directly related to the amount of electrical input to motor 41. The precise relationship, linear or otherwise, between the signal strength and load movement depends on the size and shape of the feedback grooves.

It should also be noted that, due to the fact that the end areas of piston rods 121 and 123 that are exposed to reservoir pressure are different, piston 119 comes to rest at a balance of forces, not pressures. If, however, the reservoir pressure is atmospheric pressure, then the pressure on clevis 124 will effect a precise compensation and piston 119 will come to rest with a balance of pressures in lines 113 and 115, (assuming the load on clevis 124 exerts no force when the clevis is a rest).

Referring now to FIG. 18, there is shown a construction similar to that of FIG. 17 except no amplifier is employed. Like parts bear like reference numbers. It will be seen that variable pressures downstream of throttling spool 39 at port 27 and 29 are applied directly to load piston 119 through lines 113 and 115. Negative feedback in accordance with the invention is effected by grooves 135 and 137 in the load piston. These grooves are always in position to vent some of the pressure fluid back to the reservoir so there will be no buildup of hydraulic fluid in lines 113 and 115 sufficient to lock the system.

Referring now to FIG. 19 there is shown another embodiment of the invention adapted for a single line connection between the transmitter and receiver. The construction is similar to that of FIG. 18 in that no amplifier is used and similar to that of FIG. 2 in that the transmitter functions by variably venting the working fluid rather than by variably throttling it to effect pressure change. Reference numbers for parts similar to those of FIG. 2 will be employed, increased by 200.

The transmitter of FIG. 19 employs a manual input in the form of lever 241, which moves spool 239 axially. By this means single line 224 is variably vented to return-to-reservoir conduit 251. Venting varies in accordance with the position to land 245 relative to ports 228 and 229.

Load piston 319 is connected to one side by fluid passage 263 and flow restrictor 221 to conduit 211, which leads to the source of pressure fluid. Fluid 224 is connected to passage 263 by branch line or passage 226. The flow of fluid in this branch passage is used to vary the pressure of the fluid in passage 263 applied to one side of load piston 319. Pressure on the opposite side of piston 319 is maintained constant, e.g. by connection through passage 285 leading to a conduit connected to a reservoir. Similarly, the area at the end of piston rod 321 is connected by passage 366 to conduit 368. This conduit leads to a source of fluid pressure that may or may not be the same pressure source as is connected to conduit 211.

By varying the pressure on the variable pressure end of load piston 319 and piston 321, the pressure required on the right of load 319 and piston rod 323 can be adjusted required to make the system responsive to movement of transmitter actuator 241.

Piston rod 323 is connected to clevis 324 for actuating a load (not shown). The aperture through which the clevis extends out of the receiver housing is sealed by O-ring 326. This prevents leakage from chamber 328 at the end of piston rod 323. The chamber is connected by passage 366 to conduit 367. This conduit leads to a reservoir. In accordance with the invention, negative feedback is achieved by the use of groove 337 in piston rod 323 that variably connects chamber 328 to fluid passage 353. Fluid passage 353 is connected to line 224 and passage 226.

When actuator 241 is moved to allow venting to increase in line 224, fluid pressure drops in passage 226 causing piston 319 to move to the right as illustrated in the drawing. Such movement causes groove 337 to also move to the right whereby only its shallow left end portion connects passage 353 to chamber 328. Venting, by passage 353, is thereby reduced, raising the pressure in passage 226 and bringing piston 319 to rest.

When actuator 241 is moved to the left as shown in the drawing, venting is decreased in line 224. This results in a pressure rise in passage 226 causing piston 319 to move to the left. Such movement causes groove 337 to also move to the left whereby its deeper right ended portion connects passage 353 to chamber 328. This increases venting through passage 353, lowering pressure in passage 226 and bringing piston 319 to rest.

While the use of a single line connecting the transmitter and receiver has the advantage of structural simplicity, its operation is dependent upon the maintenance of predetermined pressure in the supply and reservoir conduits 351, 211, 368, 286, and 367. On the other hand, with the two line system previously described, only the pressure differential between the two lines is significant. Both single and dual line systems are described herein in order to illustrate the scope of the invention that is directed primarily to the negative feedback means that allows a load piston's movement to be a function of the movement of the transmitter actuator. This is true whether the actuator variably blocks a pressure source, blocks venting to a reservoir, or differentially changes the pressure in two lines.

Referring now to FIG. 20 there is shown an embodiment to the invention that is the same as that of FIG. 19, except the transmitter functions by variable throttling as in FIG. 18 instead of by variable venting as in FIG. 19. Like parts are given like numbers to the constructions shown in FIGS. 18 and 19. whereby the operation will be obvious and repeated description rendered unnecessary.

Briefly, movement of manual actuator 241 moves variable restrictor means 245 to variably throttle pressure fluid flowing from conduit 11A to line 224 and passage 226 to the right of piston 319. This causes piston 319 to move to the right or left according to whether pressure falls or rises. Negative feedback by groove 337 causes the initial pressure change in passage 226 to be eliminated, bringing the load piston to rest in a new position.

Referring to FIG. 21 there is shown an embodiment of the invention similar to that shown in FIG. 19. In this embodiment a single line is employed between transmitter and receiver and the transmitter functions by variable venting to create the desired pressure change. However, an amplifier is employed in this embodiment of the invention as was illustrated in FIGS. 2 and 17. As in FIG. 4, the amplifier, in this construction, is not provided with feedback means. Like parts are given like reference numbers.

Operationally, movement of manual actuator 241 to the right or left causes pressure to rise or fall respectively in line 224. This causes amplifier spool 101 to move to the left or right, which in turn causes load piston 319 to move to the left or right. Feedback groove 137 increases or decreases the venting of passage 153 when the piston rod 323 moves to the right or left, thereby producing negative feedback to return amplifier spool 101 to its original position and bring the load piston to rest.

It may be pointed out at this time that the feedback groove tapers in different directions according to the requirements of the particular embodiment of the invention so as to always yield negative feedback in the system. If groove 137 in FIG. 31 tapered in a direction opposite to that shown in the illustration, positive feedback would be created that would accelerate the movement of the load piston toward its limiting position in one direction or the other; instead of producing a load piston position that is a direct known function of the movement of the manual actuator.

To insure that feedback passages 153 is never blocked off completely by land 79 on the amplifier spool, a pin 401 is provided at the end of cylinder 63 which moves the amplifier spool and limits its travel.

Referring now to FIG. 22 there is shown a variation of the amplifier piston illustrated by FIG. 21, constructed to incorporate a negative feedback groove 91. Negative feedback on the amplifier may be used in addition to or in place of negative feedback on the load piston. Preferably, negative feedback is employed with the load piston whether or not it is included in the amplifier. This prevents the load piston from tending to move toward the limit of its range of possible movement as soon as the transmitter activator is moved marginally.

Referring to FIG. 23, there is shown a further variation of the amplifier shown in FIG. 21. In the embodiment of the invention illustrated by FIG. 21 amplifier spool 101 is exposed to pressure by conduit 403 from a constant pressure source that is at a lower pressure than the pressure in conduit 211. This pressure opposes the variable pressure received by passage 263, which is responsive to the transmitter and causes the amplifier piston to move.

In the variation of the embodiment of the invention illustrated by FIG. 23, left end of amplifier spool 101 is exposed to reservoir pressure received through passage 404. A helical compression spring 405 is added to provide some of the reaction force on the amplifier spool needed to bring the spool into balance with transmitter pressure. This spring eliminates the need for an additional constant pressure source by providing a bias on piston 101. It also changes the system's response characteristics, since the reactive force provided by the spring varies with its degree of compression according to Hooke's Law. The spring is disposed concentrically around a pin 407, which centers the spring and functions like pin 401 (FIG. 21) to keep land 77 at the end of spool 101 from blocking passage 409 to conduit 407. If desired, the variation of the preferred embodiment of the invention illustrated by FIG. 23 can be used in conjunction with those novel features disclosed in FIG. 22.

Referring now to FIG. 24 there is shown a further variation of the amplifier initially illustrated in FIG. 21. In this construction, end 411 of amplifier spool 101 has a reduced end area so forces on the ends of the spool can be balanced by pressure acting on the left end of the piston from conduit 406. Conduit 406 is at the same pressure as conduits 211 and 11. This modification eliminates the need for spring 405 and provides a system having a different response characteristics because the pressure on spool end 411 remains constant. This construction can be used in combination with the feedback constructions illustrated in the embodiments of the invention shown in FIG. 22.

The embodiment of the invention illustrated in FIG. 21 can be modified for use with a variable restrictor or throttling type of transmitter. Such a variation is illustrated by FIG. 25. The operation of this type of transmitter is the same, operationally, as the embodiment shown in FIG. 20. It may be noted, however, that to prevent the possibility of hydraulic locking due to leaking around control land 245 and guide land 246 the ends of the transitter cylinder are vented to reservoir pressure by conduits 513 and 515. A similar construction is used in the embodiment of the invention illustrated in FIG. 21. This variation of the preferred embodiment of the invention's transmitter illustrated by FIG. 25 can be used with any of the amplifier constructions illustrated by FIGS. 21 through 24.

FIG. 26 illustrates a commercial embodiment of the invention. In this embodiment transmitter 600 has a lever 602 connected to grooved valve rod 604 and adapted to move the valve rod to variably obstruct the flow of fluid from pressure conduit 606 through grooves 608 and 610, thus creating a pressure differential between lines 612 and 614. Differential pressure moves spool valve 618 in amplifier 620. Spool valve 618 is supplied with feedback grooves 622 and 624. Movement of the amplifier's spool valve creates a pressure imbalance between conduits 626 and 628. This imbalance of forces moves piston 630 in load cylinder 632 as has been described earlier. Piston 632 is connected to clevis 634 by rod 636. The clevis is attached to a plate 638, which is provided with a cam 640 used to actuate feedback 642. Feedback 642 has a body 643 in which is mounted a grooved valve 644. The valve is attached to a wheel 646 and constrained by spring 648 to move to a position dependent on the position of cam 640 and thus on the position of piston 630 and clevis 634. As the valve's position is varied by movement of load piston 630, lines 612 and 614 are variably vented via grooves 650 and 652 in valve rod 644 to return line 654. This venting tends to reduce the pressure imbalance acting on the amplifier's spool valve causing it to return to a neutral position and stopping movement of the load piston. Hence the clevis and the load attached to it will come to rest at a position dependent on the displaced position of the transmitter's control lever 602.

In this commercial embodiment, the amplifier spool valve and load piston both incorporates feedback means taught by the preferred embodiment of the invention. These feedback means are shown working in cooperation to produce a final clevis position that is a known function of the control lever's position. Also, since the load piston has unequal areas exposed to the differential pressures from conduits 626 and 628, the load piston will come to rest at a balance of forces on its two sides rather than at a balance of pressures in lines 626 and 628.

FIG. 27 shows an isometric view of feedback 642 along lines 27--27 of FIG. 26. Springs 648 are shown biasing roller 646, which is attached to valve rod 644, into contact with inclined form 640. The cam which is shown as being "T" shaped in this illustration, rests on lower roller 656, which is a guide roller.

FIGS. 28 and 29 illustrate sectional views of the feedback valve rod and amplifier spool valve, respectively, clearly showing the feedback grooves taught by the preferred embodiment of the invention.

FIG. 30 illustrates a second commercial embodiment of the invention. In this embodiment a rotary transmitter 700 and a rotary feedback 702 operate with an amplifier 704, which is substantially the same as amplifier 620 illustrated and described in FIG. 26, and hydraulic motor 706 to produce a rotary fluidic servo system.

Transmitter 700 has a rotatable head 701 contstrained by stop 703 (see FIG. 31) to be rotatable by wheel 705 through 180 degrees. Head 701 is mounted concentric to and rotatably on control shaft 707 so as to define therebetween an annular space 710. Inside of head 701 there is an eccentric circular groove 712. Bottom plate 709 is affixed to head 701 with screws 711. Seal rigns 713 maintain the pressure integrity of the transmitter.

Fluid under pressure is introduced from a source, not shown, to conduit 708. This pressurizes annular space 710 that is in fluid communication with eccentric groove 712. This eccentric groove, which is clearly illustrated in FIG. 31, differentially pressurizes conduits 714 and 716 that extend to the ends of radially projecting arms 706' on shaft 707, and are connected to the control inputs of fluidic amplifier 704. As conduits 714 and 716 are differentially pressurized by fluid having under pressure through their respective sections of groove 712, amplifier 704 acts to control hydraulic motor 706 by establishing differential pressures in output conduits 720 and 722. Motor 706 has a two ended output shaft. End 724 is connected to a load or indicator as may be appropriate. End 726 is connected through coupling 728 to the rotary head 730 of feedback 702. Feedback 702 is structurally identical to transmitter 700. In the feedback differentially pressurized conduits 714 and 716 are variably vented via eccentric groove 732 through communicating chamber 734 to conduit 718, which is connected to a fluid reservoir, not shown. Variable venting tends to equalize pressures in conduits 714 and 716, causing the rotation of shaft 724 of hydraulic motor 706 to cease at a position that is a known function of the rotational displacement of transmitter 700's control knob 705. Stop 703 is adapted to prevent the rotation of eccentric groove 712 in head 701 past its point of greatest flow with respect to the conduits opening into said eccentric groove from control shaft 707. A similar stop, not shown, performs the same function with respect to venting these conduits in feedback 702.

FIG. 31 is a sectional view of transmitter 700 taken along line 31--31. It illustrates the fluid communication of conduits 714 and 716 with eccentric groove 712 and shows the differential variable obstruction provided by the groove between conduit 708 and each of conduits 714 and 716. The geometry of this eccentric groove may be varied in both the transmitter and the feedback to obtain a desired feedback function between the transmitter and the load in the illustrated servo system.

Referring now to FIG. 32 there is shown a single line fluidic repeater which is similar to that shown in FIG. 19 and like parts are given like reference numbers. However, feedback is effected by variable throttling of the fluid from pressure source 368A, which may be the same a source 368 or a different source at the same or different pressure, rather than variable venting to reservoir 367 as in FIG. 19. This effects a simplifcation in the number of fluid passages required as compared with the FIG. 19 construction. This also illustrates that the feedback need not always be effected by variable venting as in the previously described embodiments. The feedback groove 337A of FIG. 32 has a reverse slope compared to that of FIG. 19 due to the fact it is operating by throttling instead of venting.

Referring to FIG. 33 there is shown a single line fluidic repeater which is similar to that shown in FIG. 19, like parts being given like reference numbers. A minor difference is that a torque motor 241A serves as an actuator in the FIG. 33 embodiment, taking the place of the manual actuator 241 of FIG. 19. More importantly, the feedback means including groove 337A and reservoir return line 366A is on the opposite side of the load piston from the variable pressure line 353 coming from the transmitter. Also, in FIG. 33 the piston end 321A is exposed to reservoir pressure rather than the reverse as in FIG. 19. In the FIG. 33 arrangement, the two sides of the piston 319 are both exposed to vented pressure fluid, vented by the transmitter on one side and vented by the feedback on the other side, and equal end areas of the piston are exposed to atmospheric or reservoir pressure, so that a balance is easily achieved without the need for a pressure source at the end of the piston rod as on FIG. 19.

FIG. 34 is the same system as is shown in FIG. 33 but illustrates a commercial embodiment as distinct from the schematic showing in FIG. 33. Like parts are given the same numbers. Also, in FIG. 34 sink and source manifold 224A is provided to which connections are made as required for both reservoir pressure and for pump pressure.

FIG. 35 illustrates a single line system the same as that shown in FIG. 20 except that the transmitter has a fixed choke 245A instead of a variable throttle valve 245. By changing the size of the choke 254A movement of this load piston can be effected. Operation would be in distinct steps rather than continuous.

FIG. 36 illustrates an embodiment of the invention which is similar to that of FIG. 5, and like parts are given like numbers. However, instead of providing feedback grooves in the pistons 77, 79 as in the FIG. 5 embodiment, feedback vent ports 88A, 90A are provided in the tips of tubes 88B, 90B in the ends of the amplifier cylinder leading back to the reservoir via passages 85, 87. The ends 92A, 94A of the amplifier piston restrict flow through ports 88A, 90A to varying degrees according to the proximity of the piston ends to the ports, thereby providing variable venting according to the position of the amplifier piston. The tubes 88B, 90B provide stops limiting axial travel of the amplifier piston, preventing it from blocking the passages 61, 63 from the transmitter.

FIG. 36 also illustrates the addition of a load feedback means inside of housing 128A (compare FIG. 1) actuated by the load via bar 125A. As the load piston, not shown but similar to that of FIG. 1, travels axially, the bar 125A connected thereto causes axial travel of bolt 127A and disc 133A secured thereto. Disc 133P variably restricts flow vent nozzles 145A, 147A according to the position of the disc relative to the nozzles. The nozzles are connected by fluid lines 141A, 153A to lines 23, 25, thereby to vent the ends of the amplifier cylinder. Disc 133A and nozzles 145A, 147A are located inside the housing 128A which is vented to the reservoir via passage 167A. The operation is like that of FIG. 1 embodiment.

Referring now to FIG. 37 there is shown a load cylinder 751 in which moves piston 753 to which is connected piston rod 755. A clevis 757 on the end of the rod provides means for making connection with a load to be driven. Fluid for moving the piston in the cylinder is supplied via fluid lines 759, 781 connected to ports 763, 765 in the side wall of the cylinder. For example, fluid lines 759, 761 could be connected to lines 113, 115 of the FIG. 21 construction in place of the piston and cylinder there shown. However, in addition to such substitution the load feedback means of the FIG. 21 construction would also be omitted for the load feedback means of the FIG. 37 construction, now to be described, would take its place. In the FIG. 37 construction the load feedback means is incorporated into the load piston and cylinder.

Referring once more to FIG. 37, piston rod 755 is tubular and is threadedly connected to a threaded hole 763 in piston 753, being sealed thereto by O-ring 765. A tubular stinger 767 is threadedly connected to a threaded socket 769 in cylinder head 771 and is sealed thereto by O-ring 770. Bore 772 at the bottom of socket 769 communicates with radial passage 771 in the cylinder head. Stinger 767 extends into piston rod 775 through the end thereof that is screwed into hole 763. Stinger 767 is sealed to piston rod 755 by O-ring 773 which provides a sliding seal.

Valve tube 775 is screwed into a threaded socket 777 beyond bore 772 in the cylinder head 771. Bore 777 in the bottom of socket 777 communicates with radial passage 779 in the cylinder head. Tube 775 is sealed to socket 777 by O-ring 781. Tube 775 extends concentrically inside stinger 776 and being of smaller outer diameter than the inner diameter of the stringer forms as annular fluid passage 783 therebetween. Passage 783 opens into the space 785 in piston rod 755. The free end of tube 767 is provided with an annular inturned radial flange whose inner periphery provides a needle valve seat 787. A needle 789 is screwed into a socket 791 in the closed end of the piston rod adjacent clevis 757. The needle is provided with one or more tapered grooves 793 on its outer periphery variably by-passing seat 787. It will be apparent that fluid lines 771, 779 in the cylinder head 771 will be interconnected via annular passage 793 in the stinger and the interior passage 799 in the valve tube, and that flow through such connection will be variably throttled or restricted by needle 789 and seat 787 according to the axial position of piston 753 in cylinder 751. When incorporated into the FIG. 21 construction, fluid lines 795, 797 would connect to fluid passage 153 and return conduit 367, and the needle valve controlled fluid path from lines 795 to 797 would provide the desired variable negative feedback means.

Referring now to FIG. 37 there is shown an application of the invention to a crane to be used for loading a floating vessel, the motion of the vessel being compensated whereby the crane operator can load the vessel much the same as if the vessel were stationary. The general system of such compensation is already known, e.g. from U.S. Pat. No. 3,309,065-Prudhomme et al, so that is need be described only briefly. Crane 801 includes a support means 803 which may be a fixed or mobile platform but in any case affixed to land or sea floor. A cab 805 is pivotally mounted on the platform for rotation about vertical axis. A boom 805 is pivotally mounted on the cab for swinging up and down about a horizontal axis. Motor means not shown are provided for rotating the cab and moving the boom up and down. A cable 807 is wound on a power winch (not shown) mounted in the cab. The free end of the cable passes over pulleys 809 811 on the end of the boom and thence down to a hook 815 supporting load 817 over floating vessel 817.

Hydraulic servo motor 819 includes therewithin a piston 821 having a rod 823 extending up toward cable 807. The rod 823 is provided at its upper end with a pulley 825 adapted to pull a bight in the cable as shown at 827 in dashed lines. The length of the bight is controlled in accordance with the up and down motion of the vessel 817 by means of transmitter 829.

Transmitter 829 is mounted on arm 831 pivotally mounted at 833 on a bracket 834 for swinging up and down about a horizontal axis, this bracket being mounted on platform 803 to be turnable about a vertical axis at 835. Servo cylinder means 837 is provided for adjusting the elevation of arm 831.

The transmitter has a drive stem 839 which is moved axially in accordance with the vertical position of vessel 817 by line 841. One end of line 841 is connected to arm 831. The line passes between pulleys 843, 845 mounted on drive stem 839 and a pole 847 affixed to arm 831. The line extends down and is attached at its other end to weight 849 resting on vessel 817. As the vessel falls, the weight 849 tensions the line, moving drive stem 839 out from transmitter 847. As the vessel rises, the tension in the line is reduced and the stem 830 moves back into the transmitter under the action of bias springs.

Referring now to FIG. 39 there are shown the details of the transmitter 829 and the servo motor 819 and the means connected therebetween, all in accordance with the invention. The system of FIG. 39 is operationally generally similar to that of FIG. 1 in that it includes a transmitter 829, amplifier with feedback, and load piston and cylinder 819 with feedback, for which reason the like parts will be given the same numbers as in FIG. 1 plus 900. Thus there is a source of pressure fluid 911, flow restricing orifices 913, 915, and output lines 961, 963. Vent lines 923, 925 lead to vent ports 927, 929 in transmitter cylinder 931. The ports open at the side of valve rod 939. Rod 939 has oppositely tapering longitudinal grooves 943, 945 extending along the length thereof aligned with ports 927, 929 whereby flow out of vent ports 927, 929 is variably restricted according to the axial position of valve stem 839 in accordance with the rise and fall of the vessel 817 (FIG. 38). Two spring loaded relief valves 932, 934 venting to the hydraulic sump prevent excessive pressure build up in cylinder 931. A seal 936 is provided at the end of cylinder 931 where valve stem 839 enters. A key-way 936 disposed at ninety degrees from grooves 943, 945 extends longitudinally of valve rod 939 the same distance as grooves 943, 945 and receives pin or key 938 extending inwardly from cylinder 93 to prevent rotation of rod 939, thereby keeping grooves 943, 945 aligned with ports 927, 929.

Suitable biasing means such as compression spring 940 bearing at one end against sealed piston 944 carried by extension rod 946 urges valve stem 939 to the left from the neutral position illustrated in which both vent ports 927, 929 are equally open or restricted. Spring 942 bears at its opposite end against washer 948 resting against pins 950. Travel of piston 944 is limited by screw plug 952 in the end of cylinder 931. A vent 954 to the hydraulic sump prevents pressure build-up in the cylinder 931 between plug 952 and sealed piston 944. When valve stem 839 moves from the position shown, ports 927, 929 are unequally opened or restricted, thereby creating a pressure differential between transmitter output lines 961, 963.

Lines 961, 963 lead to amplifier cylinder 965 in which moves free piston 967 between stops 966, 968 which prevent the piston from blocking the lines 961, 963 where they enter the cylinder. The details and operation of the amplifier 964 are the same as those of the amplifier of FIG. 1 and need not be described further. It may be noted, however, that because there are pairs of vent grooves 989, 991 at each end of piston 967, radial play is balanced out, radial movement tending to close up one of vent grooves 989 causing opening of the companion groove 989, and the same holds true for vent grooves 991. Instead of pairs of diametrically opposite vent groove, other numbers of azimuthally spaced vent grooves could be employed such as three at 120 degrees, four at 90 degrees, etc., to effect balancing out of the effects of radial play.

Output lines 1113, 1115 lead from the amplifier to servo motor 819 comprising load cylinder 1117 and load piston 1119. These function the same as the load cylinder 117 and piston 119 of the FIG. 1 embodiment, moving piston rod 822 back and forth in accordance with the movement of transmitter valve rod 839, thereby shortening and lengthening bight 827 to compensate for up and down motion of vessel 817 (FIG. 38).

The load feedback means 1128 is similar to that of FIG. 1 except that vent grooves 1135, 1137 are formed on opposite sides of an extension 1133 of piston rod 823, the cylinder 1131 in which the extension moves being an extension of the load cylinder 1117. The cylinder chambers are separated by seal 1129. Similar to the construction of transmitter 829, ports 1147, 1149 through the wall of cylinder 1131 cooperate with vent grooves 1135, 1137 and connect to lines 1151, 1153 leading back to the transmitter. The load piston 1119 is positively positioned hydraulically so no venting springs are required.

It will be noted that all of the various vents for the transmitter output lines 961, 963 are in parallel. In particular, the transmitter vents, the amplifier feedback vents, and the load feedback vents are all in parallel. Fluid being vented by the amplifier feedback vents does not flow through the flow restrictions of the transmitter vent system or those of the load feedback system. Fluid being vented by the load feedback vents does not flow through the restrictions of the transmitter or the amplifier feedback vents. Fluid being vented by the transmitter does not flow through the amplifier feedback restrictions or the load feedback restrictions. This makes possible multiple feedbacks which otherwise would be very difficult if not impossible to design. This independence of the several venting systems is an important feature of this invention.

Referring now to FIG. 40 there is shown an embodiment of this invention in a servo control for a swash plate, e.g. a swash plate controlling a pump or motor. Servo controls for swash plates broadly stated are already known, for example, as disclosed in U.S. Pat. No. 3,302,585 to Adams et al, so that the swash plate pump need not be disclosed in great detail. The system disclosed herein will serve, however, to illustrate certain further variations of the subject servo system as well as the particular applicability of the subject system and its parallel independent feedback system for control of the angle of a swash plate.

The system includes a transmitter 1201, an amplifier 1203, servo motor means 1205, swash plate 1207, motor/pump 1209, and load feedback 1211. Except for the swash plate load, the system is similar to that of FIG. 1 and analogous or like parts will be given the same number as in FIG. 1 plus 1200.

The transmitter includes valve body or cylinder 1231 in which moves double tapered needle 1239. Needle 1239 is actuated manually by lever 1241 although motor means, e.g. as employed in FIG. 1 could be used if desired. The needle is urged to central or neutral position by springs 1240, 1242 disposed around the ends of the needle, the ends being enlarged to guide the needle in its axial travel within cylinder 1231. Suitable sealing means, not shown, is employed to seal between the ends of the needle and the cylinder. If desired, the centering springs could be omitted in which case the transmitter would be like that of FIG. 26.

According to the position of actuator lever 2141 and the resultant axial position of needle 1239, its tapered portions enter more or less into the valve seats 1244, 1246 to variably obstruct or throttle fluid flow from pressure fluid lines 1223, 1225 to reservoir port 1251. Lines 1223, 1225 are supplied from from pressure fluid source 1211 through flow restrictors 1219, 1221. The transmitter output lines 1261, 1263 are connected to amplifier 1203.

Amplifier 1203 includes cylinder 1265 within which moves free piston 1267. The ends of the piston are exposed to the pressures in lines 1261, 1263. Two lands 1277, 1279 at the ends of the piston are each provided with one, preferably two or more equiazimuthally spaced tapered grooves 1289, 1291 which vent pressure fluid from transmitter output lines 1261, 1263 to the reservoir through ducts 1285, 1287 in an amount varying according to the axial position of piston 1264. Helical compression springs 1289, 1291 urge the piston 1264 to its midposition. If the piston is displaced by pressure differential between lines 1261, 1263, it moves only an amount sufficient to restore balance. Balance is restored by reduced pressure differential caused by venting through feedback vent grooves 1289, 1291 and by increased and opposing differential spring force from springs 1289, 1291. The relative magnitude of these two balance restoring effect will depend on the spring constants and degree of precompression, if any, and on the size and shape of the vent grooves and the like. The spring could be omitted altogether, in which case the construction would be like that of the amplifier of FIG. 26.

It is to be noted that the venting of the lines 1261, 1263, by the feedback grooves 1289, 1291 is in parallel with the venting effected by the transmitter. Fluid passing from lines 1261, 1263 going through the restrictions of transmitter needle 1239 to the passage 1257 for return to the reservoir does not pass through the restrictions of feedback grooves 1289, 1291. This parallel arrangement is advantageous over systems such as shown in U.S. Pat. No. 2,709,421 to Avery wherein the amplifier feedback is in series with the transmitter. In the series arrangement, the effect of the feedback depends on the amplitude of the transmitter input. Like light bulbs in series, if one is out, the whole string is out. With the parallel arrangement herein disclosed, an additional transmitter 1201A may be provided in parallel with the transmitter 1202 across lines 1261, 1263, enabling the system to be controlled from either of two spaced apart stations whereat are located the respective transmitter. As many paralleled transmitters can be employed as desired.

The piston 1207 of amplifier 1302 has two loads 1307, 1308 which, as in a spool valve, control flow pressure fluid from duct 1205 to ducts 1313, 1315 leading to the swash plate 1205 constituting the load. At this point the system differs somewhat from the system of FIGS. 2 and 26 in that the output lines from the amplifier do not go to opposite sides of one load piston of a simple piston and cylinder means but instead go to two cylinders 1317, 1318 in which travel pistons 1319, 1320. However, pistons 1319, 1320 are interconnected by piston rods 1321, 1323 pivotally connected to the pistons and to flat circular disc or swash plats 1207. The swash plate 1207 is pivotally mounted at diametrically opposite points, e.g. as at 1322, in a fixed supporting frame or trunnion cradle 1324. The load in the system therefore includes a compound piston and cylinder means wherein the action of the two pistons 1319 and 1320 is not independent, the pistons being linked together via the swash plate.

Absent any pressure differential between lines 1313 and 1315, the Helical centering springs 1328, 1330 disposed in cylinders 1317, 1318 position the swash plate with its face plane 1332 perpendicular to the axis of shaft 1334. The springs each bear at one end against one of the pistons and at the other end against a washer or ring 1336, 1338 which in turn are adapted to bear against shoulders 1341, 1342 in the cylinder walls. The springs may be under a certain amount of precompression effected by screws 1344, 1346 which are screwed into the pistons and whose heads engage the washers. The cylinders are provided with extensions 1348, 1350 into which the screws can extend when the associated spring is compressed, as shown in the case of spring 1328. On the other hand, if the swash plate displacement exceeds the precompressed length of the spring, the associated screw and washer keep the spring in contact with the piston as shown in the case of spring 1330.

The motor/pump unit 1209 includes the aforementioned shaft 1334 mounted for rotation in bearings 1360, 1362. A cylinder block 1364 is keyed to shaft 1334. A plurality of pistons 1366, e.g. two, four, six, or eight or even an odd number such as one or three are mounted each in one of plural bores 1368 in the cylinder block. Piston rods 1370 connect the piston 1366 with pivoted shoes or cam followers 1372 bearing against the face of 1332 of the swash plate or end cam 1207. As the rotating shaft 1334 turns the cylinder block, the pistons 1366 are moved in and out and function as a pump with respect to fluid in lines 1390, 1392. For example fluid would be drawn in through line 1390 and expelled through line 1392 via valve plates 1392, 1394. Ported valve plate 1394 is stationary and connected to lines 1390, 1392. Valve plate 1396 is affixed to the cylinder block and rotates with it. The ports in rotating plate 1396 communicating with the several cylinder 1368 are at appropriate times in register with the appropriate ones of the ports in the stationary valve plate 1394 that communicates with the respective lines 1390, 1392 so as to effect the desired pumping action. By pumping fluid in at 1392 and out at 1390, the device becomes a motor. Whether operating as a motor or a pump, adjustment of the swash plate angle varies the volume of piston displacement. In addition to the feedback from the amplifier, load feedback 1211 is provided. The feedback valve 1211 is the same as that shown at 642 in FIG. 26, but it is driven by swash plate 1207 to which it is pivotally connected at 1398. The load feedback 1211 is in parallel with the amplifier feedback. As feedback needle 1400, which is double tapered or else provided with multiple tapered grooves, is moved axially by the swash plate, the degree of restriction at ports 1404, 1406 between port 1402 that goes in the fluid reservoir and ports 1408, 1410 that go to the transmitter output lines 1201, 1203, is varied in a direction to negate pressure changes caused by the transmitter, the same as in the case of the amplifier feedback, thereby to bring the swash plate to rest. Absent the load feedback, the swash plate would be balanced only by the action of the springs 1328, 1330, even with the amplifier balanced by its own feedback, but with the additional load feedback reliance upon the springs is not necessary.

A previously known swash plate control similar to that above described but using mechanical or electrical feedback is disclosed in catalog 625 believed to have been published about 1973 by MOOG Inc. Controls Division, Pioneer Airport, East Aurora, New York, entitled MOOG Electric Controller For Sundstrand Hydrostatic Drives; see especially pages 7-10. See also U.S. Pat. Nos. 3,065,735--Charles Jr. et al and 3,228,423 to Moog, Jr. However, the Moog catalog is not believed to teach rebalancing of the amplifier and load by negative feedback of fluid pressure as herein disclosed, and such fluid feedback is believed to be advantageous e.g. in allowing greater distance between load or amplifier and transmitter, than is feasible mechanically, and in being more reliable than electrical feedback, especially in certain environments.

Optionally, indication of the position of the swash plate may be provided by driving an indicator 1420, e.g. from the load feedback valve needle. As shown, a rod 1422 connected to the valve needle moves core 1424 relative to the coils 1426 of a linear voltage differential transformer (LDVT) to produce a voltage proportional to displacement. The voltage can drive a galvanometer to indicate swash plate position.

A modified form of swash plate angle control system is shown in FIG. 41. The system is similar to that of FIG. 40 except for the transmitter and load feedback, and ports the same as in FIG. 40 are given like numbers.

Instead of using manual actuation for the swash plate angle control system as shown in FIG. 40, an electric actuator is used in FIG. 41. Such actuator is the same functionally as that shown in FIG. 1, in view of which like parts on given the same numbers plus 1500, and further description rendered unnecessary. The connecting fluid passages are given the same numbers as in FIG. 40. It is to be observed in comparing the various embodiments, that in same cases, e.g. as in FIGS. 40 and 41, the fluid passages, e.g. from the pump, feed not only one devise, e.g. the tranmitter, but also feed another devise, e.g. the amplifier, by using enlarged annular passages in the valve block, e.g. of the transmitter, as manifolds for transmitting fluid around the transmitter the amplifier instead of having separate lines for transmitter and amplifier as in FIG. 1, but there are all functionally equivalent.

In the embodiment of FIG. 41, the swash plate controlled motor/pump unit is connected to a load cylinder 1417 similar to cylinder 17 of FIG. 1 and to cylinder 632 of FIG. 26. If desired, the cylinder could be exactly like that shown in FIG. 26 in that the cylinder could be connected to a cam actuated feedback valve like feedback 643. Instead, however, the load piston rod 1523 is connected by swivel 1524 to tension spring 1524. Spring 1524 is connected to the core or needle 1533 of feedback valve 1528. The other end of needle 1533 is connected to lines or spring 1526, which is shorter than spring 1524. The other end of spring 1526 is connected to cylinder 1517. By this arrangement the travel of needle 1533 is proportional to but less than that of piston 1523. Except for the manner in which it is driven, feedback valve 1528 is the same as feedback valve 643 of FIG. 26.

In the system of FIG. 41, the swash plate motor/pump unit functions as a variable hydraulic amplifier or servo motor controlling load piston 1519 in load cylinder 1517. The swivel connection between the load feedback valve 1528 and load piston rod 1523 allows whatever is connected to rod 1523 to rotate about the rod axis without interference from the load feedback.

Although two servo motor means 1205 are shown, in the preferred embodiments, for moving the swash plate, it is to be understood that a single servo motor means could be employed, eg. the device 117 of FIG. 1 could be connected to the swash plate via piston rod 123.

Referring now to FIG. 42 there is shown an application of the invention to the drive mechanism for a seismic generator of the type known to the trade under the trade-mark Vibroseis. For disclosure of the details of method and apparatus employed in the Vibroseis system see U.S. Pat. Nos.

System 2,680,124--Doty et al Trucks 3,024,861--Clynch 3,306,391--Bays c.f. 3,306,392--Kilmer Couplers 3,143,181--Bays 3,159,232--Fair 3,159,233--Clynch et al 3,205,971--Clynch 3,329,930--Cole et al 3,286,738--Cherry et al 3,291,249--Bays 3,365,019--Bays Vibrators 3,059,483--Clynch 3,282,372--Brown 3,372,770--Clynch Servo System 3,361,949--Brown

Referring to FIG. 42 there is shown the rear portion of an automobile or truck having a chassis or body frame 1701 and rear wheels 1703 which are connected to the truck frame by conventional means not shown. A ground engaging plate 1705 is resiliently pressed against the earth's surface 1707 by coil springs 1709 which react against I-beams 1711 carried from the truck frame by piston rods 1713. The piston tods are connected to pistons 1715 which move in compressed air cylinders 1717. By means of the piston and cylinder means 1715-1717, the truck chassis can be jacked up to place any desired amount of the truck weight on the springs 1709, or the plate 1705 can be elevated off the ground 1707 to enable the truck to move to a new location.

Connected to plate 1705 is a rigid framework 1721 including vertical posts 1723 and horizontal struts 1725. The struts are connected to the ends 1821, 1823 of a load piston rod 1822 like the ends 21, 23 of the load piston rod of FIG. 1. The piston rod 1822 carries a piston 1819 affixed thereto which moves in load cylinder 1817. The load cylinder is connected by hydraulic lines 1813, 1815 to cylinder 1865 of an amplifier which is the same as the amplifier including cylinder 65 of FIG. 1. A transmitter, not shown, like the transmitter of FIG. 1, applies pressure differentials to the amplifier in response to an electrical input like input 111 of FIG. 1. By applying an oscillating electrical input to the transmitter actuator, the amplifier and load piston respond to cause struts 1725 to move up and down. Cylinder 1817 is unattached to the truck frame, being supported only by air pressure in the cylinder at the opposite sides of piston 1818. The cylinder is sufficiently massive that a desired amount of movement of piston 1819 and plate 1705 is created by the variation of pressure differential in the cylinder on opposite sides of the piston.

The amplifier cylinder 1805 is affixed to the load cylinder 1817. A load feedback means or unit 1828 like load feedback means or unit 128 of FIG. 1 is affixed to the amplifier and is driven by a load feedback rod 1825 like rod 125 of the FIG. 1 embodiment. The feedback stabilizes the operation of the servo amplifier, controlling the load oscillations to be proportional to at least some degree of the amplitude of the electrical oscillations fed to the transmitter input.

Heretofore, Vibroseis units have been driven with electro-hydraulic systems similar to that shown in the aforementioned MOOG catalogue. The present improvement relates to the utilization of the FIG. 1 system in conjunction with a Vibroseis seismic generator.

Referring now to FIGS. 43 and 44 there is shown another modification of the apparatus shown in FIG. 1 suitable for simultaneous control of two servo systems. Such an arrangement is useful in four wheel drive trucks, for example, as shown in FIG. 43. A diesel engine D.E. may drive a gear box G which in turn drives two hydraulic pumps P which in turn drive hydraulic motors M. One motor may drive the two front wheels FW and the other the two rear wheels RW, in each case through a differential D. The pumps may be of the swash plate type shown in FIGS. 40 and 41, with variable angle swash plates, the angle of the swash plate of each pump being controlled by a separate amplifier A, the two amplifiers being controlled by the two outputs of one dual transmitter T.

Referring now more particularly to FIG. 44, the dual transmitter comprises two transmitter valves having a common valve core and valve cylinder with a single actuating means and is otherwise the same as the constructions previously described, e.g. as described in connection with FIG. 26. Therefore the same reference numbers are used as in FIG. 26 with the addition of A or B for the two system. Based on the foregoing and remembering that P stands for pump or pressure and that R stands for reservoir or return where marked on the drawing and having references to the usual hydraulic system, it is believed the operation of the system will be clear.

In operation, movement of manual actuator 602AB will shift both transmitter valve cores 604A and 604B to create differential pressures between both pairs of output lines 612A, 614A and 612B, 614B. In turn the two amplifier spools 618A, 618B will be shifted to control their output lines 626A, 628A and 626B, 628B. The loads connected to the two pairs of amplifier output lines will then be shifted, e.g. two sets of swash plates of the type shown in FIG. 40 or two load pistons of the type shown in FIG. 26 at 632. Feedback from the amplifiers is effected by vent grooves at 622A and 622B. Load feedback is effected by each load, e.g. swash plate or piston rod, being connected to one of the load feedback valve cores 644A or 644B, thereby variably venting lines 612A and 614A and lines 612B and 614B in parallel with the amplifier vent grooves.

Since the two transmitters are tied together mechanically, the two servo systems will follow in unison.

Another example of the utility of two servo systems working together is the case of twin rudders on a ship. Also in connection with shipboard use is the case of two or more Davits or booms operating to haul in a long object. In some dual load applications it may be desirable to ensure that one load does not move until the other is out of the way. In such case a master and slave system as shown in FIG. 45 may be employed. In general the servo systems, both master and slave, are like those shown in FIG. 26, so the same reference numbers are used in FIG. 45 except for the addition of M or S to indicate master or slave unit. However, opportunity is taken in FIG. 45 to illustrate two modified forms of amplifier feedback in one of which the feedback grooves are in the cylinder rather than in the piston and in another of which the feedback vent control is external to the amplifier, in either case making it possible to provide pressure equalization grooves around the pistons or lands of the amplifier valve.

In operation, actuator 602M is moved to change the position of the master transmitter 600M. The differential pressure between lines 612M, 612S thus created shifts master amplifier spool valve 618M. The latter is brought to equilibrian by its own master feedback provided by vent grooves 622M and by the master load feedback. The shifted amplifier valve varies the fluid supplied to the master load cylinder 632M causing it to move the load connected at 634M. At the same time the master load feedback 624M driven by cam 640M varies the venting of lines 612M 614M to assist in restoring balance to the amplifier. When the load feedback is sufficient, the amplifier returns to its neutral position and further fluid flow to the load cylinder ceases, the load piston then coming to rest.

Meanwhile, movement of the load piston 630M, working through cam 640M, also varies the position of slave transmitter 600S whose valve core is an extension of the valve core or needle of the master load feedback 624M.

Motion of the slave transmitter moves the spool of slave amplifier 618S which in turn varies the fluid flow to slave load cylinder 630S. The initial motion of the slave amplifier is proportional to the motion of the slave amplifier due to the slave amplifier feedback provided by external vent valves 622S. When the load has moved a proportional distance, the slave load feedback 624S, driven via cam 640S will have brought the slave amplifier back to neutral by restoring pressure balance between lines 612S and 614S. At this time the slave load piston will stop moving, having shifted a distance equal or proportional to or any other desired function of the movement of the master piston.

Note that both the master and slave amplifier valve spools are provided with annular pressure equalizing, antistick grooves 619M, 619S. Such grooves are previously known, per se, but this use is difficult if the feedback is effected by tapering grooves in the amplifier piston. By putting the feedback grooves in the cylinder as in the master amplifier, or by providing external feedback valves 622S as in the slave amplifier, it seems possible to provide the amplifier spool with the desired pressure equalizing grooves.

Referring to the feedback on the slave amplifier, it may be added that the amplifier spool is provided with extensions 621S which extend through sealed apertures in the ends of the spool valve cylinder and through apertures in feedback valve bodies 623S. The annular grooves 622S on the extensions 621S permit fluid flow to the reservoir from the continuation of lines 612S, 614S in varying amounts depending on their axial position relative to cylinder 625S.

Alternative amplifier feedbacks of the external type which permit grooving of the spool loads for pressure equalization are shown in FIGS. 46, 47, and 48. Basically these amplifiers are the same as those of FIG. 1 and like or analogous parts will be given the same number plus 1900. Instead of vent grooves 89, 91 as in FIG. 1, the FIG. 46 amplifier employs vent passages 1989, 1991 which connect the reservoir passages 1985, 1987 to the ends of the amplifier free piston or spool. Such connection is made via reverse nozzles 1990, 1992 which protrude into the spares at the ends of cylinder 1965. In operation, when the piston or spool 2001 is shifted axially, the ends of the piston approach or recede from the inverse nozzles making flow thereinto easier or more restricted, thereby providing the desired negative feedback.

In the amplifier of FIG. 47 the amplifier is similar to that shown in FIG. 46 except that the inverse nozzles 1990A, 1912A are provided in the piston itself, as are the vent passages 1989A, 1991A. The vent passages include axial portions leading from the nozzles to plural radial passages opening into cylinder 1965. Axially adjustable threaded obstructor pins 1986, 1988 protrude into the ends of cylinder 1965 through O-ring seals. By means of these pins the degree of restriction provided to flow into nozzles 1990A, 1992A can be adjusted. Lock nuts hold the pins in the desired adjusted positions.

FIG. 48 shows a further variation of the amplifier which is similar to the FIG. 47 amplifier except that the nozzles 1990A, 1992A are omitted and the ends of the adjustable obstructor pins, e.g. as shown 1986A, are tapered and extended into the vent passages in the pistons, e.g. the vent passage 1989B. This slows the rate of change of venting versus axial movement of the amplifier piston or spool compared to the arrangements of FIG. 46 and 47.

Referring once more to FIG. 46, there is also illustrated a dual transmitter. However, instead of the transmitter being of the axially moving type shown in FIG. 44, a transmitter similar to the rotary transmitter of FIGS. 4 and 5 is employed and the same reference numbers are used for the transmitter as in FIGS. 4 and 5. The difference lies in the addition of two extra nozzles 27B, 29B for controlling an additional servo system (not shown) by varying the pressure differential between the additional pair of output lines 23B, 25B.

FIG. 46 also shows a rotary type load feedback means 2202 employing an obstructor body 2204 having a threaded shaft 2206 working in threaded opening 2208 in the feedback housing 2210. The shaft is rotated by lever 2212 connected to the load (not shown) to be turned as the load rotates. Axial travel of obstructuor body 2204 caused by its rotation causes it to approach and recede from vent nozzles 2214, 2216, thereby variably to vent passages 1961, 1963 to reservoir return line 2216 and provide the desired system feedback.

Radial Play Neutralization

In the previously described systems and apparatus wherein various axially extending feedback grooves were employed in the amplifier spool, such grooves are preferably plural in number and equiazimuthally disposed around each land, as in FIG. 6-8, or inside each cylinder portion adjacent such land, as in the master amplifier of FIG. 44, in order to neutralize the effect of radial play of the spool within the cylinder. For a like reason, transmitter and feedback venting means, e.g. as in FIG. 26, preferably include plural, equiazimuthally spared grooves on the valve cores. In a rotary transmitter or feedback the desired result of neutralizing the effect of radial play can be obtained by using plural equiazimuthally spaced ports, as illustrated in FIG. 49, 50, and 51. The construction there shown also illustrates another form of dual transmitter for simultaneous control of two servo systems from a single actuator.

As shown in FIG. 49, an actuating lever 2301 is fastened by a pin 2302 to a shaft 2303. Lock rings 2304, 2305 hold the shaft against axial motion relative to cylinder body 2320 within which the shaft turns. The lock rings bear against washers adjacent the body 2320 which may be undercut to hold felt seals. However, O-rings 2306, 2307 provide the primary seals between the shaft and the cylinder. The shaft includes a pair of cylindrical bearing lands 2308, 2309 and a plurality of partial cylindrical lands 2313, 2314, separated by cylindrical grooves 2310, 2311, 2312. As seen in FIGS. 50 and 51, lands 2313 and 2314 are undercut below full cylindrical diameter on opposite sides of each land, at 2322-5, over an area of approximately 100 degrees on each side. The undercut portions are of variable depth of undercut, tapering from both ends toward the middle.

Fluid passages 2315, 2316, 2317, 2318 in body 2320 each communicate through two braches, as shown in FIGS. 50 and 51 with ports A, A.sup.1, B, B.sup.1, C, C.sup.1, D, D.sup.1, at opposite sides of the inner periphery of the cylindrical bore 2321 in body 2320. Another fluid passage 2319 communicates with the interior of bore 2321 adjacent groove 2211 below the undercut lands 2313, 2314. The branching ends of the passages 2315, 2316, 2317, 2318, are thus placed in communication with return to reservoir fluid passage 2319 in varying amounts according to the rotational position of shaft 2303, thereby to create pressure differentials between the pairs of output lines 2315, 2316 and 2317, 2318 of the dual transmitter. Any radial play between shaft 2303 and bore 2321 will be neutralized since flow through one branch of each of lines 2315, 2316, 2317, 2318 will be increased thereby and the other decreased.

It will be understood that the pairs of transmitter lines 2315, 2316, and 2317, 2318, will be connected to a source of fluid pressure having a drooping pressure versus fluid flow rate characteristic the same in FIG. 1 (pump 11, restrictors 19, 21) so that variation of the restriction to flow dependent on the positions of undercut areas 2322-5 on the otherwise cylindrical lands 2308, 2313, 2314, 2309, will effect the desired change in pressure differential between the output lines of the transmitter. The undercut areas on the lands 2313, 2311 are arranged so that after only a slight rotational movement from the neutral position shown, some of the ports A-D, A.sup.1 -D.sup.1 will be blocked completely so that the pressure differential variation caused by further rotation will be due solely to gradual enlargement of the pathways to the other ports. This is believed to work best. However, if desired, the undercut areas could be arranged so that the closure of the ports would be gradual at the same time the other ports are gradually opened.

Two-Line Transmitter That Can Vent One Line At A Time

It has been noted in reference to the embodiment of FIG. 1 and in reference to the embodiment of FIGS. 49-51 that, in connection with a two-line system, i.e. one in which the fluid pressure on both sides of the responder can be varied, it is sometimes preferred to have the transmitter vent the pressure fluid of both lines, but only of one line at a time. Because only one line is vented at the transmitter, the overall pressure of the fluid within the system is higher. Thus, a smaller flow of fluid from the pump is required to produce power making the system more efficient. In FIG. 1, such a transmitter is an axially movable spool. In FIGS. 49-51, such a transmitter is of the rotary type, but the transmitter of FIGS. 49-51 vent both lines when the transmitter is in the neutral position. FIGS. 52-54 illustrate several embodiments of rotary transmitter for two-line systems, such transmitters directly varying the pressure in only one line at a time even while in the neutral position.

1. One Operator Controls Either Line (FIGS. 52 and 52A)

As shown in FIGS. 52 and 52A, transmitter 5200 is used to control the axial movement of piston 5201 of responder 5202 by varying the pressure of the fluid in conduits 5203, 5204. Transmitter 5200 includes cylinder body 5205 having cylindrical bore 5206 therethrough. Outlet conduit 5207 communicates with bore 5206 near the center of bore 5206 and extends radially from bore 5206 to port 5207' at the base of body 5205. Inlet conduits 5208, 5209 communicate with bore 5206 through oppositely facing nozzles 5210, 5211, respectively, at points near the center of bore 5206. The tips of nozzles 5210, 5211, are tangent to the wall of bore 5206. The axes of nozzles 5210, 5211 are along a diameter of bore 5206 perpendicular to the axis of outlet conduit 5207. Inlet conduits 5208, 5209 extend from nozzles 5210, 5211 to ports 5212, 5213, respectively, at the base of body 5205.

Transmitter 5200 also includes shaft 5214 which is disposed within bore 5206 and extends from bore 5206 on either side of body 5205. Actuating lever 5215, which controls transmitter 5200, is fastened to shaft 5214 by pin 5216. Lock rings 5217, 5218 restrict axial motion of shaft 5214 relative to cylinder body 5205 of transmitter 5200. Lock rings 5217, 5218 bear against washers adjacent body 5205. Body 5205 may be undercut adjacent the washers to hold felt seals.

Shaft 5214 also includes cylindrical bearing lands 5221, 5222 and partial cylindrical land 5223. Lands 5221, 5222 are positioned at either end of bore 5207 and have O-rings 5219, 5220 which form the primary seals between shaft 5214 and bore 5206.

Partial cylindrical land 5223 is disposed directly above outlet conduit 5207 and between nozzles 5210, 5211 and is separated from lands 5221, 5222 by cylindrical grooves 5224, 5225. As shown in FIG. 52A, land 5223 is undercut below full diameter at 5226, 5227. When transmitter 5200 is in its neutral or centered position as shown by the solid lines, undercut portion 5226 extends from point K on the periphery of land 5226 through which the axis of outlet conduit 5207 extends to point Q directly beneath nozzle 5210, and undercut portion 5227 extends from point P to point L directly beneath nozzle 5211. The undercut portions are of variable depth of undercut, tapering from both ends of the particular undercut portions toward the middle.

Partial cylindrical land 5223 is biased to the neutral or centered position by means of springs 5250, 5251 attached between cylinder body 5205 and lever 5215. Movement of lever 5215 is limited by stops 5252, 5253 attached to body 5205.

When incorporated into a system as shown in FIG. 52A, inlet conduits 5208, 5209 are connected to conduits 5203, 5204 and outlet conduit 5207 is connected to the system reservoir. When transmitter 5200 is in the neutral position, nozzles 5210, 5211 are completely blocked by land 5223. Thus, neither conduit 5203 nor conduit 5204 is vented by transmitter 5200. Since no venting occurs in either line, piston 5201 of responder 5202 will be centered.

As lever 5215 is moved to position A as shown by the dotted lines of FIG. 52A, land 5223 turns counterclockwise whereby nozzle 5211 comes into communication with undercut portion 5227. As a result, the pressure in conduit 5204 will decrease an amount dependent on the depth of undercut portion 5227 along the axis of nozzle 5211. As such depth increases, the blocking effect of land 5223 decreases, causing increased venting of conduit 5204 and decreased pressure of fluid within conduit 5204. At the same time, nozzle 5210 remains completely blocked by land 5223 causing a pressure differential between conduits 5203 and 5204. In response to the pressure differential, piston 5201 moves to the right until the venting by feedback grooves 5228, 5229 in piston 5201 negates the pressure differential. If, when piston 5201 is centered as shown, no venting occurs through feedback grooves 5228, 5229, then the pressure differential is negated when venting through feedback groove 5228 equals that through nozzle 5211.

Although for most purposes, pressure losses along conduits 5203, 5204 may be assumed to be negligible, some loss does occur due to the flow resistance of the conduits. Therefore, if the responder and source of pressure fluid are close together but are remote from the transmitter, i.e. the conduit flow resistance between responder and source is less than that between the transmitter and source, the pressure in conduits 5203, 5204 adjacent the transmitter will be less than that adjacent the responder for equal rate of flow, and in order for venting by feedback groove 5228 to equal that through nozzle 5211, piston 5201 has to move farther than it would if there were no losses along conduits 5203, 5204. The resultant distortion of the response is sometimes undesirable. Therefore, responder 5202 may include variable restrictors 5260, 5261 for variably restricting flow from feedback grooves 5228, 5229, respectively, to the reservoir. As described more fully hereinafter in the section entitled "BALANCED LINES", subsection C entitled "Line Restrictors", with particular reference to FIG. 52A, the variable restrictors are adjusted so as to approximate the differences in conduit pressure losses between the pressure fluid source and the transmitter on the one hand and the pressure fluid source and the responder on the other hand. Variable restrictors 5260, 5261 include set screws 5262, 5263, respectively, having cylindrical restrictor pins 5264, 5265, respectively, attached thereto. As set screws 5262, 5263 are adjusted, pins 5264, 5265 move radially across conduits 5266, 5267 connecting feedback grooves 5228, 5229 to the reservoir thus restricting flow through such conduits.

If, as shown in FIG. 52A, responder 5202 is an amplifier including a valve for controlling the flow of pressure fluid to and from a load and conduits 5266, 5267 are variably restricted as described supra, it is preferred that responder piston include lands 5268, 5269 for isolating conduits 5266, 5267 from conduits 5270, 5271 through which fluid from the load drains. Such isolation is preferred because it permits fluid to drain from the load while the load is moving without any unnecessary restriction.

When used with a responder such as that shown in FIG. 52A, transmitter 5200 may be used on farm machinery, such as a tractor, for raising and lowering various trailing equipment such as a plow. The operation is easily completed simply by moving the lever in one direction or the other.

2. One Operator Controls Line Selected by Valve (FIG. 53)

a. Transmitter

Referring now to FIG. 53, an embodiment of a transmitter similar to that of FIGS. 52 and 52A is shown. In this embodiment, however, a single inlet conduit 5308 communicates with cylindrical bore 5206 through nozzle 5310. Partial cylindrical land 5323 differs from partial cylindrical land 5223 of FIGS. 52 and 52A in that land 5323 has only a single undercut portion 5326. When actuating lever 5215 is in the neutral position shown in solid lines in FIG. 53, undercut portion 5326 extends from point S directly beneath nozzle 5310 to point T approximately 85 degrees from point S and away from nozzle 5310. Undercut portion 5326 is of variable depth of undercut, tapering from points S and T toward the middle. Land 5323 of transmitter 5300 is biased in the neutral position by means of spring 5390 connected between cylinder body 5305 and lever 5215. Movement of lever 5215 is limited by stops 5391, 5391' connected to cylinder body 5305.

Transmitter 5300 of FIG. 53 further includes three-way, two-position valve 5330. Common part 5331 of valve 5330 is connected to conduit 5308 by means of conduit 5332. Conduits 5203, 5204 are connected to the switching ports 5333, 5334, respectively, of valve 5330.

As described, transmitter 5300 has an operative effect similar to that of transmitter 5200 of FIGS. 52 and 52A. FIG. 53C shows the 52A transmitter 5200 employed with the responder of FIG. 53 in place of the FIG. 53 transmitter 5300. Transmitter 5300, however, requires the operation of a valve in addition to a lever. Thus, with valve 5330 in the position shown by solid line 5335, clockwise rotation of lever 5215 toward position A causes the pressure fluid in conduit 5203 to vent through nozzle 5310 resulting in an appropriate response by the responder. In order to vent the pressure fluid in conduit 5204 with transmitter 5300, valve 5330 must be switched to the position shown by dotted line 5336.

b. Responder With Two Lines Connected to Inside of Piston

Transmitter 5300 may be used in conjunction with responder 5335 is also shown in FIG. 53C in conjunction with transmitter 5200 responder 5335 as shown in FIG. 53. Responder 5335 is disposed within cylinder body 5338 having generally cylindrical bore 5339 therein.

Responder 5335 includes a reduced diameter portion, shown as annular flange 5342, extending from the wall of the left-hand portion bore 5339 and forming cylindrical surface 5343. Cylindrical surface 5343 has annular groove 5344 centered thereon. Outlet conduit 5345 extends radially from the center of groove 5344 through flange 5342 and body 5338 to port 5346 which is connected to a system reservoir. Variable set screw restrictor 5341 is disposed in body 5338 perpendicular to conduit 5345 such that restrictor pin 5341' variably obstructs conduit 5345. Flange 5342 further has oppositely opening ports 5347, 5348, at flange side surfaces 5349, 5350, respectively, and adjacent the wall of bore 5339. Inlet conduits 5351, 5352 extend from ports 5347, 5348, respectively, to the outer surface of body 5338 where they are connected to conduits 5203, 5204, respectively.

Responder piston 5353 is slidingly disposed in bore 5339. Piston 5353 is a two-landed spool with lands 5354, 5355 engaging the wall of bore 5339 on either side of flange 5342 and generally cylindrical shaft 5356 slidingly engaging flange cylindrical surface 5343.

The axial position of piston 5353 relative to bore 5339 is dependent on the pressure differential of fluid in conduits 5203, 5204. If pressure is higher in conduit 5203, piston 5353 is moved to the left. If pressure is higher in conduit 5204, piston 5353 is moved to the right.

Shaft 5356 of piston 5353 has identical, diametrically opposed feedback grooves 5357, 5358 extending over approximately 60 percent of the length of shaft 5356. Grooves 5357, 5358 are of variable depth, being deepest at the center of shaft 5356 and decreasing linearly toward either end. The slope of the grooves is the same toward both ends.

Feedback grooves 5357, 5358 provide venting paths from conduits 5203, 5204 to the reservoir through groove 5344 and outlet conduit 5345. The venting through these paths is variably obstructed according to the axial position of piston 5353. As piston 5353 moves to the right, venting of conduit 5203 through the feedback grooves decreases and venting of conduit 5204 increases thus tending to negate the pressure differential causing such movement. Similarly as piston 5353 moves to the left, venting through grooves 5357, 5358 tends to negate the pressure differential causing such movement. When piston 5353 is centered about flange 5342, the venting of conduits 5203, 5204 through the feedback grooves is equal.

As described, supra, the responder of FIG. 53 reacts to pressure differential in conduits 5203, 5204 in a manner similar to that of other responders described. The responder of FIG. 53, however, retains the control system pressure fluid within the piston. As a result, piston 5353 can be connected by mechanical linkage to a load within the same cylinder.

For example, piston 5353 may be connected to a control valve for controlling the angle of the swash plate of a swash plate pump unit as shown in FIG. 53. The particular control valve and swash plate system enclosed within the dotted lines referenced as 5340 is old in the art. Swash plate pump unit 5336 is the same as that described in reference to FIG. 41 and reference may be had to that description for a more detailed understanding of its operation. In general, control valve 5370 controls the flow of pressure to and from cylinders 5374, 5375 of pump unit 5336 which, in turn control the angle of swash plate 5381. Mechanical linkage rod 5364 readjusts control valve 5370 so as to stop the flow of pressure fluid to the cylinders when swash plate 5381 has reached the desired angle.

c. Control Valve-Swash Plate Pump System

Control valve 5370 includes equally spaced annular grooves 5501, 5502, 5503 in right-hand portion 5500 of bore 5339, each groove having the same axial length. The axial length of grooves 5501, 5502, 5503 should be greater than the maximum extent of axial movement of piston 5353. Conduits 5504, 5505, 5506 extend radially from grooves 5501, 5502, 5503, respectively, through cylinder body 5338. Conduit 5505 is connected to a source of fluid under pressure. This source is the one that will supply pressure fluid to swash plate angle control cylinders 5374, 5375. Conduits 5504, 5506 are connected to cylinders 5375, 5374, respectively, by means of conduits 5376, 5373, respectively. Passageway 5507 extends radially through cylinder body 5338 between right-hand portion 5500 of bore 5339 and the portion of bore 5339 in which responder piston 5353 is disposed. Passageway 5507 serves both as a connection to the system reservoir and as a passageway for rod 5364 and, therefore, has a relatively large axial length.

Feedback piston 5363 having cylindrical bore 5509 extending axially therethrough is axially movably disposed in right-hand portion 5500 of bore 5339 and extends in part from right-hand portion 5500 toward responder 5341 and above passageway 5507. Feedback piston 5363 has diametrically opposed ports 5366, 5367 extending radially therethrough and communicating with groove 5504, diametrically opposed ports 5368, 5369 extending radially therethrough and communicating with groove 5506, and diametrically opposed ports 5371, 5372 extending raidally therethrough and communicating with groove 5505. The axial spacing of the center of each pair of ports of feedback piston 5363 is equal to the axial spacing of the centers of grooves 5504, 5505, 5506. Thus when ports 5366, 5367 are centered over groove 5504, ports 5368, 5369 are centered over groove 5506 and ports 5371, 5372 are centered over groove 5505. Ports 5366-5369 have equal diameters.

Feedback piston 5363 is connected to swash plate 5381 by means of mechanical linkage rod 5364. Rod 5364 extends through passageway 5507 and connects to feedback piston 5363 at ball-and-socket joint 5508. Rod 5364 rotates about grounded pin 5383 such that as the angle of swash plate 5381 changes, feedback piston 5363 moves axially in bore 5339. According to the configuration shown in FIG. 53, as swash plate 5381 rotates clockwise about pin 5383, feedback piston 5363 moves to the left and as swash plate 5381 rotates counterclockwise about pin 5383, feedback piston 5363 moves to the right. Preferably the orientation of rod 5364 is such that when ports 5367, 5371, 5369 are centered over grooves 5501, 5502, 5503, respectively, swash plate 5381 is in the neutral position wherein the pump output is zero. According to FIG. 53, swash plate 5381 is in the neutral position when it is vertical.

Cylindrical internal piston 5357 having bore 5510 extending axially therethrough is disposed in bore 5509 of feedback piston 5363. Internal piston 5357 has cylindrical bearing lands 5511, 5512, each having axial width equal to the diameters of ports 5366-5369. The spacing between the centers of lands 5511, 5512 is equal to the axial spacing between the centers of ports 5366, 5367 and ports 5368, 5369. According to this design it can be seen that when land 5512 is centered over ports 5366, 5367, land 5511 is centered over ports 5368, 5369. When land 5512 is positioned to the right of ports 5366, 5367, ports 5366, 5367 are in communication with the reservoir through passageway 5507 and ports 5368, 5369 are in communication with the source of pressure fluid through conduit 5505 and ports 5371, 5372. When land 5512 is positioned to the left of ports 5366, 5367, ports 5366, 5367 are in communication with the source of pressure fluid and ports 5368, 5369 are in communication with the reservoir through bore 5510 of internal piston 5359, bore 5509 of feedback piston 5363, and passageway 5507.

Internal piston 5357 is mechanically linked to responder piston 5353 by rod 5365. Rod 5365 is connected to internal piston 5357 at bore 5510 in such a manner that it will not obstruct fluid flow through bore 5510. The length of rod 5365 should be such that when piston 5353 is centered about flange 5343 and swash plate 5381 is in its neutral position, lands 5511, 5512 are centered over ports 5366, 5368, respectively.

Referring to FIG. 53, the operation of control valve 5370 in conjunction with swash plate pump unit having output conduits 5621, 5623 and driving load motor 5337 is as follows. As piston 5353 moves to the right from the position shown, internal piston 5359 is forced to the right by mechanical linkage 5365. As a result, ports 5366, 5367 communicate with conduit 5505 and fluid under pressure flows through conduit 5373 to cylinder 5374 of swash plate pump unit 5336. At the same time, ports 5368, 5369 communicates with the reservoir and fluid under pressure flows from cylinder 5375 of swash plate pump unit 5360 and through conduit 5376 to the reservoir. This fluid flow causes piston 5379 of swash plate pump unit 5336 to move to the left and piston 5380 of swash plate pump unit 5336 to move to the right which, in turn, causes swash plate 5381 to rotate counterclockwise about pin 5382. This forces bar 5364 to rotate clockwise about pin 5383 causing feedback piston 5363 to move the right until land 5512 is centered over ports 5366, 5367 and land 5511 is centered over ports 5368, 5369 thus substantially stopping further fluid flow to and from cylinders 5374, 5375. This, in turn, stops rotation of swash plate 5381 about pin 5382. It should be noted, however, that even though lands 5511, 5512 are centered over their corresponding ports, they will not completely block the ports. Some leakage of fluid will occur to either side of lands 5511, 5512 which will, in turn, result in some modulation of swash plate 5381 and feedback piston 5363. Thus, even when swash plate 5381 is in a relatively stable position, there is at least some communication between cylinders 5374, 5375 and the source of pressure fluid.

A similar, though opposite, chain of action occurs when responder piston 5353 moves to the left.

The output of pump unit 5336 may be used to drive motor 5337 which, in turn, may be used to drive a piece of rotating equipment such as a cable reel. The connection between motor unit 5337 and pump unit 5336 may be such that (1) when swash plate 5381 is in a vertical position, motor unit 5337 is stopped, (2) as swash plate 5381 rotates from the vertical in a clockwise direction, motor unit 5337 turns in a clockwise direction with increasing speed, and (3) as swash plate 5381 rotates from the vertical in a counterclockwise direction, motor unit 5337 turns in a counterclockwise direction with increasing speed.

The use of transmitter 5300 in conjunction with the responder and load system of FIG. 53 is as follows. When lever 5215 is in the neutral position as shown, neither conduit 5203 nor conduit 5204 is vented by the transmitter regardless of the position of valve 5330. Therefore, pressure exerted by fluid in conduits 5203, 5204 against lands 5354, 5355 of piston 5353 is equal and piston 5353 will be centered about flange 5342 so that feedback venting of conduits 5203, 5204 is equal. Thus, swash plate 5381 will be vertical and motor 5337 will be stopped.

If valve 5330 is in the position shown by solid line 5335 and lever 5215 is moved toward position A, conduit 5203 will be vented partially by transmitter 5300 causing responder piston 5353 to move to the right. The amount of such movement will depend on the distance lever 5215 is moved and will increase until the center of undercut 5326 is positioned at the axis of nozzle 5310. As described, supra, the rightward movement of responder piston 5353 will cause swash plate to rotate counterclockwise whereby the shaft of motor 5337 will rotate counterclockwise. Because the distance moved by piston 5353 increases with the distance moved by lever 5215 until the maximum is reached, the extent of counterclockwise movement of swash plate 5381 increases with the distance moved by lever 5215. Therefore, the rate of rotation of the shaft of motor 5337 is essentially directly proportional to the distance moved by lever 5215.

If valve 5330 of transmitter 5300 is in the position shown by dotted line 5336 and lever 5215 is moved toward position A, the ultimate position of responder piston 5353 will be to the left or center causing swash plate 5381 to rotate clockwise from the vertical and, in turn, causing the shaft of motor 5337 to rotate in a clockwise direction. Again, the speed of rotation of the shaft of motor 5337 is essentially directly proportional to the distance moved by lever 5215.

Because the same control and the same restrictor, e.g., land 5323, are used for venting both lines, the rate of clockwise rotation of the shaft of motor 5337 is substantially the same as the rate of counterclockwise rotation for a particular position of lever 5215.

Load control valve 5370 as described, supra, is designed for operation under ideal circumstances in which the response delay is negligible. As a result, such a load control valve renders a system wherein the angle of the swash plate follows closely the position of transmitter lever 5215. Furthermore, such an embodiment of a load control valve is simple enough to permit an easy understanding of the operation of the swash plate in respect to the present invention. Practically speaking, however, such an embodiment of a load control valve is not preferred because it is unstable and causes excessive modulation of the swash plate after each position change of the transmitter lever. The preferred embodiment is different from the above described embodiment in that the axial distance between the axial centers of lands 5511, 5512 is less than rather than equal to, the axial distance between the centers of ports 5366, 5368, preferably 1/16 inch less. As a result, when the midpoint between the lands is positioned over port 5371, i.e. centered, the axial center of land 5512 is positioned 1/32 inch to the right of the center of ports 5366, 5367 and the axial center of land 5511 is positioned 1/32 inch to the left of the center of ports 5368, 5369 (using the orientation of FIG. 53). In such position, the inner portions of lands 5511, 5512 overlap the mouths of the corresponding ports whereas the outer portions of lands 5511, 5512 underlap the mouths of the corresponding ports. This creates a dead region, or dwell, in the neutral position, i.e., initial movement of the transmitter causes no response by the responder. Also there is a slight leak to reservoir in the centered position.

In this preferred configuration, internal piston 5359 will be centered only when the system is in neutral. In the centered position cylinders 5374, 5375 will both be in communication with the reservoir whereby, if the neutral position is maintained, the pressure in both cylinders will be at the reservoir level. Furthermore, if piston 5353 is moved less than 1/32 in either direction by operation of the transmitter, pump unit 5336 will not move from the neutral position because neither cylinder 5374 nor cylinder 5375 will be in communication with the source of pressure fluid. Once piston 5336 has been moved more than 1/32 inch off its neutral position, however, the pump unit output will follow the movement of the transmitter.

It should be noted that by virtue of the orientation of lands 5511, 5512 of the preferred embodiment, whenever swash plate 5381 has assumed a substantially steady, non-neutral position, the ports connected to the swash plate angle control cylinder having the higher fluid pressure will be substantially blocked, and the ports connected to the swash plate angle control cylinder having the lower fluid pressure will be in communication with the reservoir. Swash plate 5381, however, is held in a relatively stable position by virtue of a hydraulic lock. Even when this preferred embodiment of the load control valve is incorporated in the system, however, there is some leakage to either side of the land that is substantially blocking its corresponding ports. This leakage results in minimal modulation of the swash plate and the feedback piston. Thus, even when swash plate 5381 is in a relatively stable, non-neutral position, there is at least some communication between the swash plate angle control cylinder having the higher fluid pressure and the source of pressure fluid.

d. Pressure Override Control

For many applications, the pressure produced by swash plate pump unit 5336 must be limited below its actual capacity in order to prevent damage to motor 5337 or some other portion of the load, or to prevent the creation of a dangerous situation such as excessive load speed. Therefore, the system may include pressure override control 5600 for detecting pump output pressure and automatically shutting off the supply of pressure fluid to cylinders 5374, 5375 of swash plate pump unit 5336 before the pressure becomes excessive. The shut off pressure is referred to herein as the critical pressure.

The override control as shown in FIG. 53 and enclosed in dotted lines 5600 is old in the art. Control 5600 includes cylinder body 5602 having cylindrical bore 5604 therein. Bore 5604 has ends 5610, 5611. Passageway 5606 extends radially through body 5602 from the wall of bore 5604 at a point near the center of bore 5604. Passageway 5606 is connected to conduit 5505 of load control valve 5370 by means of conduit 5608.

Passageway 5612 extends radially through body 5602 from the wall of bore 5604 at a point spaced axially from passageway 5606 toward end 5611 of bore 5604. Passageway 5612 is connected to a source of fluid under pressure. This source will become the source to which conduit 5370 of the controller is connected which, in turn, is the source of pressure fluid for pistons 5374, 5375 of swash plate pump unit 5336.

Passageway 5613 extends radially through body 5602 from the wall of bore 5604 at a point adjacent end 5610 of bore 5604. Passageway 5613 is connected to the system reservoir.

Cylinder body 5602 also has narrow relief conduit 5615 extending radially through body 5602 from end 5611 of bore 5604.

Cylinder body 5602 further includes ball check valve chamber 5614. Chamber 5614 has a generally cylindrical shape with hemispherical ends 5616, 5618. The axis of chamber 5614 is perpendicular to that of bore 5604. Passageways 5620, 5622 extend through body 5602 from hemispherical ends 5616, 5618, respectively, along the axis of chamber 5614. Passageway 5620 is connected to swash plate output conduit 5621 by means of conduit 5625. Passageway 5622 is connected to swash plate output conduit 5623 by means of conduit 5627.

Ball 5626 having a diameter slightly less than that of chamber 5614 is disposed in chamber 5614 such that it may move from one hemispherical end to the other. When ball 5626 is positioned in a hemispherical end as shown, it effectively isolates chamber 5614 from the passageway extending from such hemispherical end. Thus, when pressure of fluid in output conduit 5621 is greater than that in output conduit 5623, ball 5626 is forced into hemispherical end 5618 whereby output conduit 5623 is isolated from chamber 5614. The pressure within chamber 5614 then will be equal to that of conduit 5621. If the pressure of conduit 5623 is greater than that of 5621, ball 5626 is forced into hemispherical end 5616 and the pressure within chamber 5614 will be equal to that of conduit 5623. Thus, the pressure within chamber 5614 generally is that of the output conduit having the greatest pressure.

Body 5602 also has cylindrical piston passageway 5624 which extends axially from end 5610 of bore 5604 to the center of ball check valve chamber 5614.

Cylinder body 5602 further has threaded passageway 5628 extending axially from end 5611 of bore 5604 through the wall of body 5602. Set screw 5630 having slot 5632 at its outer end is threadingly disposed in threaded passageway 5628. Cylindrical land 5634 is attached to the inside end of screw 5630.

Spool 5636 having shaft 5638 and cylindrical bearing lands 5640, 5644 is disposed in bore 5604 and piston passageway 5624. Lands 5640, 5644 are each in sealing, sliding engagement with bore 5604. Land 5644 is positioned at the end of shaft 5638 nearest land 5634 attached to set screw 5630 and is separated from land 5634 by spring 5646 forming a variable length spring chamber 5647. Cylinder body 5602 has bleed passageway 5617 extending radially therethrough from the general center of spring chamber 5647. Land 5640 is positioned at the other end of shaft 5638.

Spool 5636 also includes stop cylinder 5641 attached axially to land 5640 on the side opposite shaft 5638. Stop cylinder has a diameter greater than that of piston bore 5634 but substantially less than that of bore 5604. The axial length of stop cylinder 5641 is such that when it rests against end 5610 of bore 5604, land 5640 is positioned between passageways 5613, 5606, preferably as close as possible to passageway 5606 without interfering with fluid flow between passageway 5606 and bore 5604.

The arrangement of lands 5640, 5644 and cylinder stop 5641, therefore, permits axial movement of spool 5636 within bore 5604. Piston stop 5641 limits movement of spool 5636 in one direction and land 5644, in combination with land 5634 and spring 5646, limits movement of spool 5636 in the other direction.

Spool 5636 further includes piston 5648 extending axially from the end of stop cylinder 5641 and into piston bore 5624 which it slidingly and sealingly engages. Preferably, the axial length of piston 5648 is such that when spool 5636 has moved toward land 5634 to the maximum extent, a portion of piston 5648 remains within piston bore 5624.

The axial position of spool 5636 relative to bore 5604 depends on the force differential of the pressure within chamber 5614 which acts against one end of spool 5636 and the force of spring 5646 which acts against the other end of spool 5636. As mentioned supra, the pressure within chamber 5614 generally will be equal to the pressure within the pump output conduit having the higher pressure. The force exerted by spring 5646 against spool 5636 will vary according to the axial position of land 5634, such position being variable by set screw 5630. In general, set screw 5630 should be adjusted such that when chamber 5614 is at reservoir pressure, piston stop 5641 rests firmly against bore end 5610, and such that when the pressure within chamber 5614 is at the critical pressure, land 5640 completely isolates passageway 5604 from passageway 5612. If, for some reason, the critical pressure changes, set screw 5630 can be readjusted accordingly.

As described, pressure override control 5600 will operate as follows. If the controller and swash plate pump unit are stable in the position shown in FIG. 53, the pressure in pump output conduit 5621 is greater than that in pump output conduit 5623 whereby the pressure in chamber 5614 is equal to that in conduit 5621. Assuming the pressure in conduit 5621 is much less than the critical pressure, cylinder stop 5641 of control 5600 will rest against bore end 5610. Thus, land 5640 does not obstruct groove 5605 and controller conduit 5505 is in full communication with the source of pressure fluid.

If the transmitter is adjusted so as to cause internal cylinder 5359 to move to the left, fluid will flow from the source of pressure fluid, through conduit 5505 and into cylinder 5375 whereby the angle of swash plate 5381 from vertical increases and the pressures in pump output conduit 5621 and in chamber 5614 increase. If the pressure in chamber 5614 becomes sufficiently high, the force exerted against piston 5624 will exceed that against land 5644 causing spool 5636 to move axially. Land 5640 will then partially obstruct groove 5605.

If the output pressure continues to increase to the critical pressure, spool 5636 will move axially until land 5640 completely blocks groove 5605 thus cutting off the flow of pressure fluid to controller conduit 5370 and connecting conduit 5505 to the reservoir. As a result fluid will flow from cylinder 5375 to the reservoir and swash plate 5381 will rotate counterclockwise. The pressure in conduit 5621 will be reduced causing land 5640 to move toward end 5610 and reconnecting conduit 5505 to the pressure fluid source. If the position of responder 5335 remains unchanged, land 5640 will modulate between either side of passageway 5604. Although such modulation does occur, the output of pump unit 5336 is maintained fairly constant at a pressure level just under the critical pressure. The pressure in conduit 5621 thus remains near the critical level until the transmitter is adjusted so as to cause swash plate 5381 to rotate about pin 5382 in a counterclockwise direction and causing the pressure in pump output conduit 5621 to decrease.

A similar reaction occurs if the pressure within pump output conduit 5323 is greater than that in conduit 5321.

It should be noted that pressure override control 5600 is to prevent the output pressure of swash plate pump unit 5336 from exceeding a certain level. Control 5600 does not stop pump unit 5336.

e. Emergency Stop Control

The system of FIG. 53 further includes emergency stop control 5650. Stop control 5650 is designed to return pump unit 5336 to neutral when, for some reason, it is desirable to stop the equipment being driven by the pump quickly and when the pump unit cannot otherwise be returned to neutral due to some malfunction within the transmitter or responder. Furthermore, emergency stop control 5650 can be implemented to return the pump to neutral when the pressure override control fails. The effect of stop control 5650 is to connect both swash plate angle control cylinders 5374, 5375 to the reservoir quickly.

Referring to FIG. 53, stop control 5650 includes cylinder body 5652 having cylindrical bore 5654 therein. Cylindrical shaft passageway 5656 extends axially from one end of bore 5654 through cylinder body 5652. Relief conduits 5658, 5660, extend radially from either end of bore 5654 through cylinder body 5652. Conduit 5662 extends radially from near the center of bore 5654 through body 5652. Conduit 5662 is connected to conduit 5664 which may be connected either directly or indirectly to controller conduit 5505. As shown in FIG. 53, conduit 5664 is connected indirectly to controller conduit 5505 through pressure override controller 5600. Such an indirect connection is used when both the pressure limiting feature of the pressure override controller is desired in addition to the emergency stop feature.

Conduits 5666, 5668 extend radially from bore 5654 through body 5652. Conduits 5666, 5668 are axially spaced equidistant to either side of conduit 5664. Conduit 5668 is connected to the system reservoir. Conduit 5666 is connected to a source of fluid under pressure. This source will become the source to which conduit 5505 of the controller is connected which, in turn, is the source of pressure fluid for pistons 5374, 5375 of swash plate pump unit 5336.

Emergency stop unit 5650 also includes three-landed spool 5670 disposed in bore 5654. Cylindrical bearing lands 5672, 5674 are positioned at either end of spool 5670 with land 5674 nearest shaft passageway 5656. Land 5676 is positioned at the center of spool 5670. Lands 5672, 5674, 5676 all form sliding seals with bore 5654.

Stop unit 5650 further includes shaft 5678 extending axially from spool 5670 and through shaft passageway 5656. Button 5680 is attached to the outer end of shaft 5678. Spring 5682 is disposed about shaft 5678 and bears at one end against cylinder body 5652 and at the other end against button 5680 thus tending to bias button 5680 away from body 5652 and to pull spool 5670 toward the end of bore 5654 from which shaft passageway 5656 extends. Shaft 5678 has annular stop 5684 positioned between land 5674 and body 5652 for limiting movement of spool 5670 so that land 5674 does not bear against the end of bore 5654.

The length of shaft 5678 and the position of annular stop 5684 should be such that when shaft 5678 is biased to its normal position as shown such that stop 5684 bears against the end of bore 5654, land 5676 is positioned between conduits 5662 and 5668, and such that when button 5680 is moved as close as possible to body, land 5676 is positioned between conduits 5662 and 5666.

Operation of emergency stop unit 5650 as described is as follows. When the unit is in its normal position as shown, conduit 5662 is in full communication with conduit 5666 and therefore controller conduit 5370 is in communication with the source of pressure fluid. If button 5680 is fully depressed, conduit 5662 is no longer in communication with conduit 5666 but, instead, is in full communication with conduit 5668. Thus the pressure at controller conduit 5370 is dropped to that of the system reservoir.

If the output pressure of the pump unit is changing, one of the cylinders 5374, 5375 is in communication with the source of pressure fluid and the other cylinder is in communication with the system reservoir. Furthermore, as noted supra, even when the angle of swash plate 5381 is in a relatively stable, non-neutral position there is some communication between the swash plate angle control cylinder having the higher fluid pressure and the source of pressure fluid. In either case, the other cylinder is simultaneously in communication with the reservoir. Therefore, if button 5680 is depressed, both cylinders will immediately come into communication with the reservoir and the force of the springs bearing against pistons 5379, 5380 will tend to return swash plate 5381 to its neutral position.

f. Adjustable Nulling Responder (FIGS. 53A and B)

As noted, supra, it is preferred that the length of rod 5365 be such that swash plate 5381 is vertical when responder piston 5353 is centered. This preference is based on the assumption that when transmitter 5300 is in the neutral position, piston 5353 is centered, which, in turn, is based on the assumption that the pressure of the fluid in conduits 5203, 5204 at ports 5347, 5348, respectively, is equal when transmitter 5300 is in the neutral position and that the venting of conduits 5203, 5204 through the feedback grooves is equal when piston 5353 is centered. Thus, when the transmitter is in the neutral position, swash plate 5381 is vertical and, as desired, the shaft of motor 5337 does not rotate. Whether these assumptions hold true, however, depends on numerous contingencies. If a minor leak exists, or if the fixed restrictions at the source are slightly different, or if there is a kink in a conduit, the assumptions may not hold true, and piston 5353 will not be centered when transmitter 5300 is in the neutral position. If it is critical for a particular application that swash plate 5381 be absolutely vertical when the transmitter is in its neutral position, slight deviance from these assumptions may produce undesirable results.

In FIGS. 53A and 53B, an alternative embodiment of the responder is shown. In this alternative embodiment the reduced diameter portion is shown as axially movable annulus 5342' rather than annular flange 5342. Because annulus 5342' forms a part of the feedback venting path, axial movement of annulus 5342' causes axial movement of piston 5353 even though the position of the transmitter is not varied. Thus, even though piston 5353 does not "center" when the transmitter is in the neutral position, annulus 5342' may be adjusted so that swash plate 5381 is in the vertical position when transmitter 5300 is in the neutral position.

Referring now to FIG. 53A, responder 5335' has axially aligned ports 5347', 5348'. Inlet conduits 5351', 5352' extend radially through body 5338' from ports 5347', 5348', respectively, and connect to conduits 5203, 5204, respectively. Bore 5339' further has port 5393 located on the circumference of the wall of bore 5339' centered between ports 5347', 5348'. Outlet conduit 5345' extends radially from port 5393 through body 5338' and connects to the reservoir. Outlet conduit 5345' is enlarged at port 5393.

Also positioned on the circumference of the wall of bore 5339' centered between ports 5347', 5348' is cam pin bore 5394 extending radially through body 5338'. Cam pin bore 5394 has enlarged diameter portion 5395 opening into bore 5339'. Cam pin 5396 is disposed in cam pin bore 5394. Cylindrical control shaft 5397 of cam pin 5396 extends through the entire length of cam pin bore 5394 and extends just above the outer surface of body 5338'. The portion of control shaft 5397 extending above the outer surface of body 5338' has slot 5398 so that control shaft 5397 can be rotated using a slot-head screwdriver.

Control shaft 5397 includes cylindrical bearing lands 5384, 5385 separated by groove 5386. Land 5384 abuts shoulder 5387 formed at the junction of enlarged diameter portion 5395 of cam pin bore 5394 with the remainder of bore 5394. Land 5386 is tangent to the surface of bore 5339. O-ring 5388 is disposed in groove 5386.

Cylindrical cam pin 5389 is attached to land 5385 and extends a short distance into bore 5339'. As shown in FIG. 53B, cam pin 5389 is arranged eccentrically on land 5385.

Annulus 5342' is sealingly and slidingly disposed in bore 5339'. Annulus 5342' has sufficient axial length to extend beyond ports 5347', 5348' at either end when centered about ports 5347', 5348'. Internal cylindrical surface 5343' of annulus 5342' is recessed over much of its length forming axially centered groove 5344'. Annulus outlet conduit 5345" extends radially through annulus 5342' from the center of groove 5344' such that when annulus 5342' is centered about ports 5347', 5348', annulus outlet conduit 5345" is aligned with outlet conduit 5345'. Because outlet conduit 5345' is enlarged at port 5393, conduit 5345" will be in full communication with conduit 5345" even when annulus 5342' is not centered about ports 5347', 5348'.

Annulus 5342' has grooves 5347", 5348" on either side and communicating with inlet conduits 5351', 5352', respectively, to permit flow of fluid from conduits 5351', 5352' to either side of annulus 5342'. The depth of grooves 5347", 5348" toward the axial center of annulus 5342' should be such that when annulus 5342' is centered about ports 5347', 5348', grooves 5347", 5348" extend a short distance beyond ports 5347', 5348".

Annulus 5342' also has slot 5399 at its axial center for accommodating cam pin 5389. Slot 5399 is sufficiently long and wide to permit cam pin 5389 to move within slot 5399 as control shaft 5396 is rotated.

Operation of the null adjustment of the alternative embodiment shown in FIGS. 53A and 53B is as follows. If, when transmitter 5300 is in the neutral position, swash plate is turned counterclockwise from the vertical, it is clear that feedback piston is positioned too far to the right. This, in turn, would be caused because internal piston 5359 and piston 5353 are positioned too far to the right when the transmitter is in the neutral position. By rotating control shaft 5396 clockwise so that cam pin 5389 moves to the left, annulus 5342' is forced to the left due to the action of cam pin 5389 against the side of slot 5399. Such movement causes feedback venting of conduit 5203 to decrease and the feedback venting of conduit 5204 to increase. As a result, the pressure of the fluid to the left of annulus 5342' increases and the pressure of the fluid to the right of annulus 5342' decreases and piston 5353 moves to the left. As piston 5353 moves to the left, internal piston 5359 moves to the left causing swash plate 5381 to rotate clockwise about pin 5383 toward the vertical. Rotation of cam pin control shaft is continued until swash plate 5381 is vertical.

If swash plate 5381 is positioned clockwise from vertical when the transmitter is in the neutral position, piston 5353 is positioned too far to the left. Cam pin control shaft is then rotated counterclockwise causing annulus 5342' to move to the right. Piston 5353 then moves to the right causing swash plate 5381 to move toward the vertical.

3. Separate Operator for Each Line (FIG. 54)

Referring now to FIG. 54, a system is shown that may be used for rotating the shafts of two motors at the same speed and in either a clockwise or a counterclockwise direction. Such a system may be incorporated into the truck described in reference to FIG. 43 such that clockwise rotation of the motor shafts results in movement of the truck in a forward direction and counterclockwise rotation of the motor shafts results in movement of the truck in a reverse direction.

Transmitter 5400 of the system is used for controlling two receivers precisely the same as those described in respect to FIG. 53. Therefore, the response of receiver 5401 is proportional to the pressure differential between the fluid in conduit 5203 and the fluid in conduit 5204; and the response of receiver 5402 is proportional to the pressure differential between the fluid in conduit 5403 and the fluid in conduit 5404. Because the system is to be used to drive the wheels of a single truck, it is desirable that the response of receiver 5401 be identical to the response of receiver 5402 at any given time. This is best accomplished by keeping the pressure of fluid in conduit 5203 essentially equal to the pressure of fluid in conduit 5403, and the pressure of fluid in conduit 5204 essentially equal to the pressure of fluid in conduit 5404.

Transmitter 5400 is well adapted for this purpose. Transmitter 5400 includes reverse unit 5405 and forward unit 5405'. Forward unit 5405 controls the pressure of fluid in conduits 5203, 5403 and reverse unit 5405' controls the pressure in conduits 5404, 5204.

Unit 5405 is substantially identical to transmitter 5200 of FIGS. 52 and 52A with only the following differences. Lever 5407 is biased to position A, referred to as the neutral position, by spring 5414. Movement of lever 5407 is limited by stops 5415, 5416. Partial cylindrical land 5409 has diametrically opposed undercuts 5410, 5411 each covering an area of approximately 40 degrees. When unit 5405 is in the neutral position, lever 5407 is in position A, undercut 5410 extends from a point just beneath nozzle 5412 which connects to conduit 5203 to a point near the center of the outlet conduit, and undercut 5411 extends from a point near the center of the outlet conduit to a point just above nozzle 5413 which connects to conduit 5403.

Unit 5405' is in all essential respects identical to unit 5405, with like parts having like reference numbers with the addition of a prime (').

Operation of transmitter 5400 is as follows. When the levers of units 5405, 5405' are both in position A, conduits 5203, 5204, 5403, 5404 are all blocked at the transmitter resulting in no pressure differential and no rotation by the motors. As lever 5407' of unit 5405' is moved toward position B, pressure fluid in conduits 5204, 5404 is vented. The extent of venting of each conduit is identical since the undercuts are identical and diametrically opposed. As a result, both responder pistons move to the left an identical amount causing the motors to rotate in a clockwise direction at an equal speed. The truck will then move forward at a speed proportional to the extent of movement of lever 5414 from the neutral position. Maximum forward speed occurs with the lever in position B whereby the center of undercuts 5410' and 5411' of land 5409' are aligned with the axis of the nozzles and with lever 5407 in of unit 5405 in neutral position A.

Reverse movement of the truck may be effected similarly by moving lever 5407 toward position B while lever 5407' is in neutral position A. Because unit 5405 is identical to unit 5405', the speed of reverse movement of the truck will be the same as the speed of forward movement of the truck for equivalent movement of lever 5407.

Clearly, the system of FIG. 54 is designed such that, for most purposes, only one of the levers of transmitter 5400 should be moved from neutral position A at a time. Movement of both levers will result in a hybrid response of the receiver which is determinable only through a consideration of the relative movement of the levers.

Although transmitter 5400 serves to make the responses of receivers 5401, 5402 very nearly identical, it is possible that the output of the pump unit of receiver 5401 is not identical to that of receiver 5402. In such a case, the front wheels of the truck would tend to turn at a different rate than the rear wheels when the truck is on the highway. This could cause excessive wear of the tires and could damage the steering. This problem is solved in the truck of FIG. 54 by attaching lines 5422, 5423 across the outputs of the pump units so that the outputs are connected in parallel. In this way, the pump outputs will be essentially identical.

Valves 5420, 5421 are disposed in lines 5422, 5423, respectively, so that the outputs of the pump units can be separated. Thus, if individual drive of the front and rear wheels is necessary, such as on rough terrain to prevent spinout, valves 5420, 5421 can be closed.

FIG. 55 shows a truck configuration similar to that of FIG. 54. Each wheel of the truck of FIG. 55, however, is driven by a separate motor. The motors, in turn, are driven by the output of four pump units. In the configuration of FIG. 55, the outputs of the pumps may be selectively connected such that each pump drives a separate motor; such that two pumps together drive two motors; such that three pumps together drive three motors; and such that all four pumps together drive all four motors. In this way, the motors can be driven together so that they turn at the same rate for highway driving and they can also be driven separately in order to prevent spinout.

Referring to FIG. 55, shaft 5570 of the diesel engine drives pump units 5571, 5572, 5573, 5574. Output conduits 5575, 5576 of pump units 5571 are connected to motor 5577 which, in turn drives front wheel 5578. Output conduits 5579, 5580 of pump unit 5572 are connected to motor 5581 which, in turn, drives front wheel 5582. Output conduits 5583, 5584 of pump unit 5573 are connected to motor 5585 which, in turn, drives rear wheel 5586. Output conduits 5587, 5588 of pump unit 5574 are connected to motor 5589 which, in turn, drives rear wheel 5590.

The outputs of pumps 5571, 5572 are connected in parallel by conduit 5591 connected between conduits 5575, 5579 and conduit 5592 connected between conduits 5576, 5580. The outputs of pumps 5572, 5573 are connected in parallel by conduit 5593 connected between conduits 5579, 5583 and conduit 5594 connected between conduits 5580, 5584. The outputs of pumps 5573, 5574 are connected in parallel by conduit 5595 connected between conduits 5583, 5587 and conduit 5592 connected between conduits 5584, 5588. Conduits 5591-5596 each has a valve V for selectively shutting off or permitting fluid flow through the corresponding conduit. If each wheel is to be driven individually, all the valves are closed so that there is no communication between the output of one pump and the output of another pump unit. If it is desirable that all four wheels rotate at the same rate, all the valves are opened completely. If it is desirable that each of the front wheels rotate at the same rate and that each of the rear wheels rotate at the same rate, but that the front wheels rotate independently of the rear wheels, the valves in conduits 5591, 5592, 5595, 5596 are opened and the valves in conduits 5593, 5594 are closed.

The technique of tying the outputs of the pump units in parallel was first conceived by the applicant on June 12, 1970. No claim to such technique is made since such technique is belived to have been in public use by another more than one year before the present application. Such use was in conjunction with the load control valve and swash plate pump unit as described (enclosed in line 5340 of FIG. 53). The load control valve was connected by rod 5365 to a WABCD (Westinghouse) servo motor which controlled the load control valve.

BALANCED PATHS

In the fluidic repeater systems described supra, the response of the load should bear some relation to the movement of the transmitter; i.e., when the transmitter is placed in a particular position, the system will not achieve steady state until the load assumes a steady position corresponding to the position of the transmitter. For example, it may be desirable to have the load at an extreme position when the transmitter is at an extreme position. It may be desirable to have the load centered between extremes when the load is centered. The response of the load to movement of the transmitter is referred to hereinafter as the load response characteristic.

A system having the desired load response characteristic may be designed by making several theoretical approximations as to the extent of venting by various variable restrictors in different positions and then applying those approximations experimentally. Further changes to a design may be made during experimentation until the desired load response characteristic is achieved.

Usually, such a design will result in a particular transmitter and a corresponding receiver. The receiver will include a responder and a feedback actuated by the responder. The responder may be a load or it may be an amplifier controlling a load. If the responder is an amplifier, there will be a feedback actuated directly by the load.

When a transmitter and corresponding receiver are commercially applied in a particular application, however, the movement of the transmitter and the movement of the load may not correspond as desired or according to the design. This departure from the design has been found to occur when the distances between the transmitter and receiver are great. In such instances, pressure losses along the conduits themselves affect the system response; i.e., the conduits offer a resistance to the flow of the fluid.

One solution for this problem would be to take these line losses into account in the design and to modify the transmitter and receiver accordingly. This procedure, however, limits the applications for which a particular system design is available since it could be used only where a particular distance between the transmitter and receiver is involved. Because substantial time and expense often is consumed in designing a system to have a precise load response characteristic, it is not economical to separately design a system for every individual application.

It has been found, however, that a system having a venting transmitter and designed to have a particular load response characteristic when the receiver and transmitter are separated by a short distance such that conduit losses are negligible may be used in applications involving significant distances between the transmitter and receiver. This is done by making the fluid resistance along a path extending from the source, through a feedback variable restrictor controlled directly by the load to the reservoir (such path referred to hereinafter as a load feedback path), exclusive of the resistance of such load feedback variable restrictor, approximately equal to the total resistance along a path extending from the source, through a transmitter variable restrictor to the reservoir (such path referred to hereinafter as a transmitter feedback path), exclusive of the resistance of such transmitter feedback variable restrictor. The total resistance along a path exclusive of the resistance of the transmitter or feedback variable restrictor along such path is referred to hereinafter as the total path resistance of that path. Such approximate equalization is referred to hereinafter as balancing.

In particular, it has been found that such balancing of the total path resistances of a transmitter and a load feedback path may be accomplished to a large extent by equalizing the total length of such transmitter and load feedback paths; by making the cross-sectional area of the conduits along the longer of such paths greater than such cross-sectional area along the shorter of the paths; or by placing additional restrictions, either fixed or variable, along the shorter of such paths.

In the one-line systems described supra, there is only one load feedback path and only one transmitter path, and therefore, the total path resistance of such load feedback path must be made approximately equal to the total path resistance of such transmitter path. In the two-line systems described supra, however, there are two transmitter paths and two load feedback paths. In such systems proper balancing to achieve the desired load response characteristic may include making both the transmitter path total path resistances equal to one another whereby both of the load feedback path total path resistances may be made approximately equal to both of the transmitter path total path resistances.

Furthermore, a two-line system may be balanced by making the total path resistance of the load feedback path of one line approximately equal to the total path resistance of the transmitter path of the other line, and the total path resistance of the load feedback path of such other line equal to the total path resistance of the transmitter path of such one line.

If, however, the responder of the system is an amplifier and there is a feedback variable restrictor directly controlled by the responder, there will be an amplifier feedback path extending from the source, through the amplifier feedback variable restrictor to the reservoir. If the total path resistance of the amplifier feedback path in a particular application is substantially the same as that for which the system was designed or if the flow of fluid through the amplifier feedback variable restrictors is very small when the system is in steady state, the system may be balanced according to the above methods without adjustment of the total path resistance of the amplifier feedback path so long as the balancing of the transmitter and load feedback paths does not affect the amplifier feedback path. Such conditions will generally exist when the source of pressure fluid and the reservoir are located adjacent the receiver or when the resistance of the amplifier feedback variable restrictors are steadystate approaches infinity, i.e., flow through such restrictors is small at steady-state. If the total path resistance of the amplifier feedback path is different from that which existed when the system was designed and the steady-state flow through the amplifier feedback variable restrictor or restrictors is not small relative to the flow through the transmitter and load feedback variable restrictors, the total path resistance of the amplifier feedback path must be adjusted independently to compensate for such change.

Specific embodiments employing the balanced path concept are discussed hereinafter.

A. Equal length paths

FIG. 56 shows a two-line system having a transmitter 6000 and a receiver 6002. Transmitter 6000 includes inlet ports 6004, 6006 and outlet port 6008. Transmitter 6000 further includes variable restrictor 6010 for variably restricting flow between inlet port 6004 and outlet port 6008, and variable restrictor 6012 for variably restricting flow between inlet port 6006 and outlet port 6008. Variable restrictors 6010, 6012 are in fixed relation with one another such that as the fluid resistance of one of the restrictors varies, the fluid resistance of the other restrictor varies inversely. The fluid resistance of restrictors 6010, 6012 is varied by lever 6014.

Receiver 6002 includes feedback portion 6016, responder portion 6018 and load portion 6020. Feedback portion 6016 includes inlet ports 6022, 6024 and outlet port 6026. Feedback portion 6016 further includes variable restrictor 6028 for variably restricting flow between inlet port 6022 and outlet port 6026, and variable restrictor 6030 for variably restricting flow between inlet port 6024 and outlet port 6026. Variable restrictors 6028, 6030 are in fixed relation with one another such that as the fluid resistance of one of the restrictors varies, the fluid resistance of the other restrictor varies inversely. The fluid resistance of restrictors 6028, 6030 is varied by the movement of cam 6032 in cooperation with wheel 6034. Feedback portion 6012 also includes responder connection ports 6036, 6038 which are in direct, unrestricted communication with inlet ports 6022, 6024.

Responder portion 6018 includes a spool valve having piston 6040 in cylinder 6042. Responder portion 6018 also includes inlet ports 6044, 6046 and outlet ports 6048, 6050. Outlet ports 6048, 6050 are connected to the system reservoir. Inlet ports 6044, 6046 are in direct, unrestricted communication with the ends of cylinder 6042. Responder portion 6018 further includes variable restrictors for variably restricting flow from ports 6044, 6046 to ports 6048, 6050, respectively. Such restrictors are shown in FIG. 56 as grooves 6052, 6054 in the ends of piston 6040 in combination with grooves 6056, 6058 in the wall of cylinder 6042. Such variable restrictors are in fixed relationship with one another such that as the fluid resistance of one of the restrictors varies, the fluid resistance of the other restrictor varies inversely. Preferably, when piston 6040 is centered with respect to cylinder 6042, the fluid restriction of such restrictors approaches infinity.

Responder portion 6018 and feedback portion 6016 are connected together by conduits 6060, 6062. Conduit 6060 extends from port 6036 and feedback portion 6016 to port 6044 in responder portion 6018. Conduit 6062 extends from port 6038 in feedback portion 6016 to port 6046 in responder portion 6018.

Load portion 6020 includes piston 6064 in cylinder 6066. Cylinder 6066 is connected to the spool valve of responder portion 6018 by means of conduits 6068, 6070. Load portion 6020 further includes piston rod 6072 which is connected to piston 6064. Piston rod 6072 is connected to cam 6032.

Receiver 6002 is connected to transmitter 6000 by means of conduit 6074 extending between port 6004 of transmitter portion 6000 and port 6022 of feedback portion 6016; conduit 6076 extending between port 6006 of transmitter 6000 and port 6024 of feedback portion 6016; and conduit 6078 extending between port 6008 of transmitter 6000 and port 6026 of feedback portion 6016. The lengths and cross sections of conduits 6074, 6076, 6078 are substantially identical to one another. Conduits 6074, 6076, 6078 have ports 6080, 6082, 6084, respectively, at a point representing the center of the length of the particular conduit and dividing each conduit into an A part and a B part. Port 6084 is connected to the system reservoir. Ports 6080, 6082 are connected to either end of conduit 6086, the center of which is connected to the system source of pressurized fluid. Conduit 6086 has fixed restrictor 6088 between its center and port 6074 and fixed restrictor 6090, having the same fluid resistance valve as restrictor 6088, between its center and port 6076.

According to the embodiment of FIG. 56 as described, fluid flows from the source to the reservoir along four basic paths when the system is in steady-state. The first transmitter path extends from the center of conduit 6086, through restrictor 6088, conduit part 6074B, variable restrictor 6012, and conduit part 6078B to the reservoir. The second transmitter path extends from the center of conduit 6086, through restrictor 6090, conduit part 6076B, variable restrictor 6010, and conduit part 6078B to the reservoir. The first load feedback path extends from the center of conduit 6086, through restrictor 6088, conduit part 6074A, variable restrictor 6028, and conduit part 6078A to the reservoir. The second load feedback path extends from the center of conduit 6086, through restrictor 6090, conduit part 6076A, variable restrictor 6030, and conduit part 6078A to the reservoir.

The total path resistance along these four paths essentially will be the resistance offered by the fixed restrictor, which is either restrictor 6088 or 6090, plus that offered by half the length of either conduit 6074 or 6076, plus that offered by half the length of conduit 6078. The resistance offered by a conduit for laminar flow is in direct proportion to the length and cross-sectional area of the conduits. Because such lengths and cross-sectional areas are the same over each of the paths and the resistances of the fixed restrictors are equal, the total path resistances of all of the above described paths are equal. As a result, if transmitter 6000 and receiver 6002 have been designed such that the movement and position of load 6020 has a desired correspondence to the movement and position of transmitter lever 6014, such correspondence will be substantially maintained regardless of the distance separating transmitter 6000 and receiver 6002 as long as conduits 6074, 6076, 6078 meet the description of the preceding paragraph.

As noted, however, the effectiveness of equalizing the length of the lines between the source and reservoir and the transmitter, on the one hand, and that between the source and the reservoir and the receiver on the other hand is limited to systems wherein laminar flow predominates over the lines between the transmitter and receiver. In most fluidic control systems, the fluid has a high viscosity and the flow rate through the conduits is low enough that laminar flow will predominate and the above mentioned relationship will apply.

Furthermore, there will be some conduit losses within the transmitter and receiver themselves. In the first place, however, such conduits will be relatively short and such losses will be negligible. In the second place, such losses will automatically come into play when the receiver and transmitter are designed. Therefore, conduit losses within the transmitter and receiver will not adversely affect the load response characteristic.

Because responder portion 6018 is an amplifier directly controlling amplifier feedback variable restrictors, there also are first and second amplifier feedback paths, such first amplifier feedback path extending through grooves 6052 and such second amplifier feedback path extending through grooves 6054. Because the amplifier paths include flow through conduit parts 6074A, 6076A, the total path resistance of such paths will vary according to the distance between the receiver and, therefore, the total path resistance of the amplifier feedback paths will vary from that for which the system was designed. At steady-state, however, piston 6040 will be centered and the resistance offered by the amplifier (responder) variable restrictors will be nearly infinite. Thus, the flow of fluid through grooves 6052, 6054 will be low and the change in total path resistance of the amplifier feedback path will not significantly affect the load response characteristic of the system.

If, however, the centered resistance of the amplifier feedback variable restrictors is not sufficiently large and, as a result, the load response characteristic is not as desired, the total path resistance of the amplifier feedback paths must be increased to correct the discrepancy.

Furthermore, if the responder is an amplifier, as it is in the system of FIG. 56, the source of pressure fluid may also supply fluid to the load. In such a case, the source should be near the receiver so that only minimal pressure loss will occur between the source and the responder. If the embodiment of FIG. 56 is used, locating the source near the receiver results in a long line extending between the source and the point at which fluid is supplied to conduits 6074, 6076. This additional line length causes additional losses which lower the overall efficiency of the system.

The modification of the system of FIG. 56 as shown in FIG. 57 remedies this latter problem to some extent. Referring to FIG. 57, transmitter 6000 and feedback portion 6016 are connected by conduit 6092 extending between feedback portion port 6022 and transmitter port 6006; conduit 6094 extending between feedback portion port 6024 and transmitter port 6004; and conduit 6096 extending between feedback portion port 6026 and transmitter port 6008. Conduits 6092, 6094, 6096 have equal length and cross-section. Conduits 6092, 6094, 6096 have ports 6098, 6100, 6102, respectively, dividing the respective conduits into an A part and a B part. In the modification, ports 6098, 6100 are near the receiver and port 6012 is near the transmitter. The location of the ports should be such that conduit parts 6092A, 6094A, 6096B have approximately equal lengths, i.e., the short length, and conduit parts 6092B, 6094B, 6096A have approximately equal lengths, i.e., the long length. Port 6102 is connected to the reservoir and ports 6098, 6100 are connected to either end of conduit 6086.

As can be seen, the total path resistance along each of the four basic steady-state paths will essentially be equal to the resistance offered by a fixed resistor in conduit 6086 plus the resistance offered by a short length of a conduit plus the resistance offered by a long length of a conduit. Because these resistances are equal for each of the paths, the total path resistances along each such path will equal one another.

There may be applications wherein the reservoir must be near the receiver and/or the source must be near the transmitter. Such a modification may be made as long as the total length of conduit between the receiver and transmitter along the load feedback paths and transmitter paths is equal for all such paths.

B. Balanced Cross Sections

Usually, the source derives its supply of fluid from the system reservoir. Therefore, in such cases, maximum efficiency requires locating the reservoir near the source. Furthermore, if the responder is an amplifier as in the FIG. 56 embodiment, the source should be located near the receiver in order to supply fluid to the load with maximum sufficiency. In addition, if the responder is an amplifier directly controlling amplifier feedback variable restrictors as in the FIG. 56 system, locating both the source and the receiver near the reservoir has the advantage of making the amplifier feedback paths short no matter how great the distance between the transmitter and receiver. As a result, the total path resistance of the amplifier feedback paths may be kept at the value for which the system was designed and such total path resistance need not be adjusted according to the distance between the transmitter and receiver.

If the system uses equal length lines as described in the preceding subsection, however, locating the reservoir near the source and near the receiver will result in a long line connecting either or both the reservoir and the source to the control system. As a result, some of the efficiency sought to be gained will be lost. In addition, the amplifier feedback path total path resistance will be increased, thus making adjustment to such total path resistance necessary.

In the embodiment shown in FIG. 58, however, the source and reservoir can be located near the receiver and connect to the control system near the receiver. As a result, the only long lines are the conduits connecting the transmitter to the receiver.

Referring to FIG. 58, feedback portion 6016 is connected to transmitter 6000 by conduit 6104 extending between feedback portion port 6022 and transmitter port 6006; conduit 6016 extending between feedback portion port 6024 and transmitter port 6004; and conduit 6108 extending between feedback portion port 6026 and transmitter port 6008. Conduits 6104, 6106, 6108 are of equal length. Conduits 6104, 6106, 6108 have ports 6110, 6112, 6114 respectively, dividing the respective conduits into an A part and a B part such that conduit parts 6104A, 6106A, 6108A are of equal length and conduit parts 6104B, 6106B, 6108B are of equal length. Port 6114 is connected to the reservoir. Ports 6110, 6112 are connected to either end of conduit 6086, the center of which is connected to the source.

Because the pump and reservoir are to be connected to the control system at a point near the receiver, ports 6110, 6112, 6114 are located relatively near the receiver. As a result, conduit parts 6104A, 6106A, 6108A are shorter in length than conduit parts 6104B, 6106B, 6108B and both of the transmitter paths are longer than the feedback paths. Because the fluid resistance of a conduit is proportional to the length and cross-sectional area of the conduit, if the conduits have constant cross-sectional area, the total resistance along the transmitter paths would be greater than that along the feedback paths. If, however, the cross-sectional areas of conduit parts 6104B, 6106B, 6108B are made larger than those of conduit parts 6104A, 6106A, 6108A, such total resistance along the transmitter paths can be made equal to that along the feedback paths. Such a differentiation in cross-sectional area is shown in FIG. 58.

The precise difference in the cross-sectional areas of the A part of the conduits and the B part of the conduits will depend on the difference in their respective lengths. The laminar flow fluid resistance of a circular conduit is directly proportional to the length and inversely proportional to the cross-sectional area of the conduit. Therefore, if the conduits have circular cross-section and, if the B part of the conduits is twice as long as the A part of the conduits, the cross-sectional area of the B part of the conduits must be twice that of the A part of the conduits.

Because conduits 6104, 6106, 6108 have varying cross-sectional areas over their length, there will of necessity be points where the conduit changes from one cross-sectional area to another. See, for example, point 6116 of conduit 6104. Such a point may extend over the entire length of the conduit with the cross-sectional area over a part of the conduit being the average of cross-sectional areas over that part's length, or it may be an abrupt ridge such as where tubes of different cross-sectional areas are welded together. Tubes having variable cross-sectional areas over their entire length are not readily available and may not be practical. On the other hand, an abrupt ridge will cause turbulent fluid flow as opposed to laminar thus resulting in a departure of the relaionship between resistance and conduit length and cross-sectional area. As a result, use of a conduit having such an abrupt ridge or balancing cross-sectional areas may not result in the desired load response characteristic. Therefore, the preferred embodiment includes short variable cross-sectional area sections which provide a gradual change over a short portion of the conduit as shown.

It should be noted that when balancing the paths by varying conduit cross-sectional areas, if the system includes amplifier feedback variable restrictors controlled directly by the responder acting as an amplifier, the balancing should be done by increasing the cross-sectional area of the conduits extending to the transmitter rather than reducing the cross-sectional area of the conduits extending to the receiver. This is due to the fact that reducing the cross-sectional area of the receiver conduits, i.e., conduit parts 6104A, 6106A, 6108A, may cause the total path resistance of the amplifier feedback path to vary from that for which the system was designed thus necessitating independent adjustment of such total path resistance even though the total path resistances of the transmitter paths and the load feedback paths have been made equal.

Although the system described shows the source and reservoir conduit connections near the receiver, the balanced cross-section concept is equally applicable to systems wherein the distance between the receiver and transmitter significantly affects the response of the load response characteristic movement and the source and reservoir are to be located nearer one of such components than the other.

Furthermore, the concept is also applicable to systems wherein the reservoir and source are to be connected to the system at different locations as long as the total conduit resistance along each source-to-reservoir path is equal to such resistance along all the other such paths, such resistances being made equal by appropriate adjustment of cross-sectional area of the conduits to account for different conduit lengths.

C. Line Restrictors

Referring to FIG. 52A, described in detail supra, a fluidic repeater system is shown wherein the total path resistance along the transmitter and load feedback paths are made equal by means of restrictors positioned along the shorter of the paths. As noted supra, page 64, responder 5202 in FIG. 52A is an amplifier. Unlike the system of FIG. 56, however, the desired load response characteristic is concerned with the position of the amplifier rather than the component controlled by the amplifier. Therefore, the responder, although an amplifier, is considered to be the load for path balancing purposes. Such a system is desirable where the precise position of the responder piston affects the speed of a hydraulic motor controlled by the amplifier. Therefore, unlike the system of FIG. 56, the path balancing occurs along the feedback paths which include the feedback variable restrictors controlled by a responder acting as an amplifier.

The system of FIG. 52A is designed for applications wherein the source and reservoir are to be located closer to the receiver than they are to the transmitter. In such a case, the load feedback paths will be shorter than the transmitter paths and, if all the conduits have the same cross-sectional area, the total path resistance along the load feedback paths will be less than that along the transmitter paths.

Variable restrictors 5260, 5261, therefore, are placed along the feedback paths in order to increase the resistance along such paths. Although the precise configuration of such variable restrictors may vary, the preferred embodiment includes set screws 5262, 5263 having pins 5264, 5265, respectively, secured thereto. Set screws 5262, 5263 are in threaded engagement with the cylinder body such that as they are rotated, pins 5264, 5265 move transversely across conduits 5266, 5267, respectively, thus variably restricting flow through such conduits.

Because this is a two-line system, proper balancing may be theoretically accomplished by adjusting restrictor 5260 so that the total path resistance along the load feedback path which includes restrictor 5260 is made equal to the total path resistance of the transmitter path which extends through a portion of conduit 5204, and by adjusting restrictor 5261 so that the total path resistance of the load feedback path which includes restrictor 5261 is made equal to the total path resistance of the transmitter path which extends through a portion of conduit 5203.

In actual practice, however, such adjustment is virtually impossible. In the first place, the flow at the variable restrictors will in all likelihood be turbulent. As a result, the fluid resistance of the restrictors will vary according to the fluid flow rate by the restrictors and, therefore, the total path resistance of the load feedback path can not be set to a single value. In the second place, even when the fluid flow rate at the restrictor is known, the actual value of the fluid resistance of the restrictor for that flow rate may be determined only by complex computation. Proper balancing may, however, be most nearly achieved by adjusting the variable restrictions after the system is installed until the deviations at the extreme positions of the load are as small as possible and are equal for either extreme. Usually, when this response is obtained, the total path resistance of each load feedback path will be very nearly equal to that of the corresponding transmitter path when the transmitter and load are both centered between such extreme positions.

Because of the turbulent flow caused by the variable restrictors, the total path resistance of particular feedback path will not be equal to that of the corresponding transmitter path for all flow rates, although it can be made approximately equal over the entire flow rate range so as to greatly improve the load response characteristic. In general, however, a system that is balanced using variable restrictors will not give as accurate a load response characteristic as is possible when the equal length lines or balanced cross-section concepts are employed. Thus, while the variable restrictor balance line embodiment is preferred where adjustability is a desirable feature, the equal length and balanced cross-section embodiments may be preferred where precision is a principally desirable feature.

Referring again to FIG. 52A, responder 5202 of the FIG. 52A system has bypass venting conduits for the load so that the load venting will not be restricted by variable restrictors 5260, 5261. Such conduits are shown at 5270, 5271. Conduits 5270, 5271 are isolated from conduits 5266, 5267, by additional lands 5268, 5269 on Section 5201. Lands 5268, 5269 are disposed between conduits 5266, 5270 on the one hand, and conduits 5267, 5271 on the other hand. By isolating the load venting from the load feedback venting in this way, the load response for a particular position of piston 5201 is unaffected by the resistance of restrictors 5260, 5261.

Although the path balancing concept has been shown and described in only a few configurations and for only a few types of systems, the concept is applicable to a wide variety of systems and may be applied in a number of ways.

For example, the feedback paths of a two-line system may be combined into a single conduit at a point between the feedback variable restrictions and reservoir. In such a case, an additional restrictor may be disposed in such single conduit. As shown in FIGS. 53 and 53C, conduits 5203, 5204 both vent through their respective feedback variable restrictors into conduit 5345. Therefore, a single variable restrictor 5341 may be used to vary the total path resistance along both the feedback paths until the desired load response characteristic is achieved.

Furthermore, because in most system, the source and reservoir will be located adjacent the receiver, the restrictor may be fixed rather than variable as shown in FIG. 59 which is a modification of a portion of FIGS. 53 and 53C. Such a fixed restrictor adversely affects both the adaptability of the receiver to different applications and the flexibility of the system once installed. Therefore, it is desirable to use such a fixed restriction in combination with a variable restrictor as shown in FIG. 60 which is a further modification of FIGS. 53 and 53C.

It should be noted, however, that the total path resistances of the two load feedback paths of the FIGS. 53 and 53C systems are not separately adjustable. Therefore, precise balancing of the paths requires that the total path resistances of the two transmitter paths equal one another. All the transmitter variable restrictors and all the load variable restrictors are disposed near one another whereby even without balancing the paths, the total path resistances of both transmitter paths are very nearly equal and the total path resistances of both feedback paths are very nearly equal. In such cases, the single adjustment of the FIGS. 53 and 53C embodiments will suffice.

In some cases, however, this equality may not exist. Therefore, not only must the feedback paths be balanced with the transmitter paths, but also the transmitter paths must be balanced with one another.

As shown in FIG. 54, for example, the transmitter variable restrictors may be remote from one another. Thus, for receiver 5401, the transmitter variable restrictor for one line (5203) is in transmitter unit 5405 and the variable restrictor for the other line (5204) is in transmitter unit 5401. If the transmitter units are remote from one another, the total path resistances of the two transmitter paths may be substantially different. Therefore, transmitter unit 5405 includes set-screw variable restrictor 6166 for variably restricting the transmitter path that includes conduit 5203 and transmitter unit 5405' includes a set-screw variable restrictor 6168 for variably restricting the transmitter path that includes conduit 5204. Variable restrictor 6166 is appropriately adjusted so that the total path resistance of the transmitter path that includes restrictor 6166 is made approximately equal to the total path resistance of the load feedback path that includes a portion of conduit 5204, and variable restrictor 6168 appropriately adjusted so that the total path resistance of the transmitter path that includes restrictor 6168 is made approximately equal to the total path resistance of the load feedback path that includes a portion of coduit 5203. Again, as with the FIG. 52A system, such path resistances are made approximately equal by adjusting the restrictors of the installed system until the deviations at the extreme positions of the load are made as small as possible and equal at either extreme.

If, as in the FIG. 56 embodiment, the load feedback paths combine immediately after the load feedback variable restrictors and separate adjustment of the transmitter path total path resistances is not desirable, the load feedback paths may be variably restricted for balancing purposes at a point along such paths between the source and the load feedback variable restrictor of each path. As shown in FIG. 61, a system includes transmitter 5200 and receiver 6124. Transmitter 5200 was described supra in connection with FIGS. 52, 52A. Receiver 6124 includes feedback portion 6126, responder portion 6018 and load portion 6020. Responder portion 6018 and load portion 6020 were described supra in connection with FIG. 56. Feedback portion 6126 is substantially the same as feedback portion 6016 described supra in connection with FIG. 56 and the parts of feedback portion 6126 corresponding to parts of feedback portion 6016 are given the numbers of such corresponding parts. Unlike feedback portion 6016, however, feedback portion 6126 does not have ports 6036, 6038 nor the conduits connecting such ports to ports 6022, 6024, respectively.

Receiver 6124 further includes balancing portion 6128 having inlet ports 6130, 6132 and outlet ports 6134, 6136. Ports 6130, 6134 are connected together by conduit 6138 and ports 6132, 6136 are connected together by conduit 6140. Flow through conduits 6138, 6140 is variably restricted by restrictors 6142, 6144, respectively.

Receiver 6124 also includes conduit 6146 connected between balancing portion port 6130 and responder portion port 6044, conduit 6148 connected between balancing portion port 6132 and responder portion port 6046; conduit 6150 connected between balancing portion port 6134 and feedback portion port 6022; and conduit 6152 connected between balancing portion port 6136 and feedback portion port 6024. Conduits 6146, 6148 have ports 6154, 6156, respectively, at some point along their respective lengths.

Receiver 6124 is connected to transmitter by conduit 6158 connected between port 6154 and transmitter port 5212, and conduit 6160 connected between port 6156 and transmitter port 5213. Conduits 6158, 6160 have ports 6162, 6164, respectively, such ports dividing their respective conduits into an A part between the conduit port and the receiver and a B part between the conduit port and the transmitter. Preferably, conduit parts 6158A, 6160A have equal lengths, such lengths being shorter than those of conduit parts 6158B, 6160B. Conduit parts 6158B, 6160B also have equal length. Conduits 6158, 6160 have a constant cross-sectional configuration over their entire lengths.

Furthermore, the system reservoir, not shown, is positioned closer to receiver 6124 than it is to transmitter 5200. The reservoir is connected by conduits, not shown, to conduit 5207 of transmitter 5200, feedback portion port 6026, and responder portion ports 6048, 6050.

Therefore, in the FIG. 61 embodiment as described, the total conduit resistance along the feedback paths is less than that along the transmitter paths. By adjusting variable restrictors 6142, 6144, however, the total path resistance of the load feedback path which include feedback portion 6126 of one line can be made approximately equal to the total path resistance of the transmitter paths.

The embodiment of the balanced path concept shown in FIG. 61 has several additional advantages over the embodiments of the concept discussed heretofore. In the first place, the balancing portion need not be built into the remainder of the receiver as is done in the embodiments of FIGS. 52A and 53. Thus the transmitter and receiver of the system may be balanced using the equal length lines, the balanced cross-section, or the line restrictors depending on the particular application. If the line restrictors are to be used, the balancing portion may be readily added to the receiver.

Furthermore, unlike the embodiments of FIGS. 56, 57, the amplifier feedback paths are not affected by the path balancing. Thus, if the source and reservoir are located near the receiver so the total path resistance of the amplifier feedback paths is unchanged from design value, the load response characteristic will depend only on appropriate balancing of the transmitter and load feedback paths; i.e., no adjustment of the total path resistance of the amplifier feedback path is necessary.

Path balancing portion 6128 may be used on different systems in a variety of ways. For example, referring to FIG. 62, the input of a balancing portion 6128 may be connected to ports 6048, 6050 of responder portion 6018 of the FIG. 56 system by conduits 6162, 6164, respectively. The output of balancing portion 6128 may then be connected to a reservoir near the receiver. Thus, if the amplifier feedback variable restrictors do not have a high resistance when piston 6040 is centered, the total path resistance of the amplifier feedback paths may be adjusted so that the desired load response characteristic is obtained.

Although the above descriptions of line balancing are limited to two-line systems, including those where the transmitter vents only one line at a time, line balancing may be used in one-line systems as well.

For example, FIG. 63 shows the use of a balancing line restrictor in the system of FIG. 21 as modified by FIGS. 22, 24 and described in detail supra. As shown in FIG. 63, set-screw variable restrictor 6170 variably restricts flow through conduit 153 which is part of the load feedback path. As shown, the source connects to the control line (conduit 224) at the receiver. Assuming the reservoir is adjacent the receiver, the total path resistance of the load feedback path, exclusive of restrictor 6170, is less than that of the transmitter path. By adjusting restrictor 6170, the total path resistance of the load feedback path may be increased until it equals the total path resistance of the transmitter path.

Furthermore, because the total path resistance of the amplifier feedback path through groove 91 may be kept the same as that when the system was designed no matter how remote the transmitter, the total path resistance of the amplifier feedback path need not be adjusted as the distance between the transmitter and the receiver varies.

Similarly, line balancing may be used in a system having two lines, one line vented only by the transmitter and the other line vented only by the feedback. For example, as shown in FIG. 64, line 6172 is connected to one side of load cylinder 6174 and to transmitter 5300, transmitter 5300 having been described in detail in connection with FIG. 53. Line 6176 is connected to the other side of load cylinder 6174 and is variably vented by grooves 6178 in piston rod 6180 to conduit 6182 which is connected to the reservoir. Conduit 6182 is variably restricted by balancing set-screw type restrictor 6184. The load feedback path extends from the source to the reservoir through conduit 6176 grooves 6178 and conduit 6182. The transmitter feedback path extends from the source to the reservoir through conduit 6172 and transmitter 5300. Assuming the length of the load feedback path is shorter than that of the transmitter path, the total path resistance of the load feedback path may be made to equal that of the transmitter path so that the desired load response characteristic is obtained.

Alternatively, the line restrictor of the system shown in FIG. 64 may be modified to comprise a fixed restrictor either in addition to or in place of variable restrictor 6184. Thus, FIG. 64A shows orifice 6250 as a fixed restrictor in series with restrictor 6184 and FIG. 64B shows orifice 6252 as a fixed restrictor in place of restrictor 6184.

Line balancing may also be used where the load feedback vents one line, the transmitter vents the other line, and the amplifier feedback vents both lines. The system shown in FIG. 65 includes transmitter 6186 which is identical to that shown in FIG. 21 and described in detail in connection therewith, and receiver 6188. Receiver 6188 includes responder portion 6190, load portion 6192 and load feedback portion 6194.

Responder portion 6190 is an amplifier substantially the same as that of the system of FIG. 1 including piston 101 in cylinder 103 and described in connection therewith. The output of responder-portion 6190 controls the movement of load piston 6196 of load portion 6192.

Load feedback portion 6194 includes conduit 6206 connected to one end of responder cylinder 6204 and in communication with grooves 6208 on piston rod 6210. Piston rod 6210 is connected to load piston 6196. Grooves 6208 are in communication with the reservoir such that as load piston 6196 moves back and forth, fluid within conduit 6206 is variably vented through grooves 6208 to the reservoir. Flow through conduit 6206 is variably restricted by balancing set-screw type variable restrictor 6212.

Receiver 6188 also includes conduits 6214, 6216 connected to either end of the responder cylinder. The other end of conduits 6214, 6216 is connected through fixed restrictors 6218, 6220, respectively, to the source of pressurized fluid. Conduit 6216 and conduit 6206 are connected to the same end of cylinder 103. Conduit 6214 has port 6222 at a point between cylinder 103 and fixed restrictor 6220.

Transmitter 6186 is connected to receiver 6188 at port 6222 by single-line conduit 6224.

According to the description, the load feedback path extends from the source, through conduits 6216, 6206, and grooves 6208 to the reservoir. The transmitter path extends from the source, through a portion of conduit 6214, through conduit 6224 and the transmitter 6186 to the reservoir. If transmitter 6186 is remote from receiver 6188, i.e., conduit 6224 is long, and the reservoir is adjacent receiver, the total path resistance of the transmitter path will be greater than the total path resistance of the load feedback path exclusive of the resistance of variable restrictor 6212. Therefore, the transmitter path and the load feedback path may be balanced by appropriately adjusting restrictor 6212 so as to increase the total path resistance of the load feedback path.

The embodiment of FIG. 65 further includes two amplifier feedback paths, one through conduit 6214 and responder piston grooves 6198, and another through conduit 6216 and responder piston grooves 6200. Again, the total path resistance of the amplifier feedback path may be left unaffected by the distance between the transmitter and the receiver as well as by adjustment of balancing restrictor 6212. Therefore, no adjustment of the total path resistance of the amplifier feedback paths is necessary even though the distance between the transmitter and receiver is large or otherwise different from that for which the system is designed.

From the foregoing description it will be apparent that a typical embodiment of the invention includes a transmitter, amplifier, and a load piston and cylinder means, with feedback means actuated by both the amplifier and by the load piston and cylinder. Sometimes the load piston and cylinder have been called a receiver, reflecting the fact that the system can be used for remote control. Depending on its position as being adjacent the transmitter or adjacent the load piston and cylinder means, the amplifier may be said to be part of the transmitter or receiver, using these terms in a broader sense. Since the element referred to as an amplifier can in some cases be replaced by a similarly functioning device which does not amplify, it has sometimes been called merely a responder. This also reflects the fact that the responder can be used directly as in indicator or load actuator rather than as a valve to control a load piston and cylinder means or servo motor. Sometimes the word responder is used more broadly to refer to all of that which follows the transmitter, in which case the amplifier or first stage following the transmitter may be called a primary piston and cylinder means and the second stage a secondary or load piston and cylinder means.

The variable pressure line or lines from the transmitter may be called its output, in that the transmitter produces a variable pressure signal that is sent out to the next stage of the system. In like manner, the fluid flow lines controlled by the valve that constitutes the amplifier or responder may be called the output of the amplifier or responder.

The foregoing explanation of the terminology used in the description and the claims will help correlate the claim language with that of the description of the preferred embodiments.

It will be apparent from the appended claims that the inventions can be viewed as including transmitter means and receiver means. Connector conduit means connect the transmitter means and receiver means and include first and second conduit means. The first or high pressure conduit means is also connected to the source of fluid under pressure. The second or low pressure conduit means is also connected to the reservoir. The receiver means includes load means, whose output displacement is to be proportional to the displacement of the transmitter means. The receiver means further includes load feedback means responsive to movement of the load means.

The load means may, for example, be a responder including a piston in a cylinder mechanically connected to a rod or arm forming the load means output. Or the load means may be a responder including a piston in a cylinder hydraulically connected to a servo motor moving a rod or arm constituting the load means output. As a further example, the load means may be a responder including a piston in a cylinder mechanically connected to a spool valve whose moving element is the load means output, the spool valve hydraulically controlling some element such as a rotary fluid motor.

In any case, the responder piston and cylinder move in response to changes in pressure in the high pressure conduit means created by venting thereof to the low pressure conduit means by the transmitter means and the load feedback means. It is the vent paths of the transmitter means and load feedback means which are to be balanced.

Usually the high pressure conduit means includes two high pressure conduits connecting to different parts of the responder cylinder to act on oppositely directed surfaces of the responder piston. The transmitter means may vary the pressure in but one of the high pressure conduits, as illustrated in FIGS. 63, 64, 65, or in both high pressure conduits simultaneously, as illustrated in FIGS. 56 and 61, or in each high pressure conduit separately as illustrated in FIGS. 52A, 53, 53C, 54.

It will also be apparent from the claims that the invention can be viewed as including a plurality of fluid paths from the source to the reservoir, each path including a portion of the high pressure or first conduit means and a portion of the low pressure or second conduit means, e.g. a path through the transmitter means and a path through the feedback means. Various ways of balancing these paths are illustrated and described.

The following is a summary of the several illustrated embodiments of the invention referred to in the claims.

______________________________________I. Balancing ConduitsFIG. NO. Type of Line Balancing______________________________________56 Source of pressure fluid and Reservoir midway between Transmitter and Feedback57 Source near Feedback and Reservoir near Transmitter58 Long Large Cross Section Lines To Transmitter and Short Small Cross Section Lines To Feedback______________________________________II. Balancing RestrictorsFIG. NO. Location of Restrictors______________________________________(a) Systems Employing Two LinesTo Transmitter54 Transmitter Line Upstream of Transmitter52A Downstream from Feedback In Separate61 Upstream from Feedback Feedback Lines Common Responder Feedback Line Downstream from Feedback:53, 53C, 54 Variable59 Fixed60 Fixed and Variable(b) Systems employing One Line to Transmitter63 Feed Back Line Upstream of Feedback acting on same line as transmitter64 Feedback Line Downstream of Feedback acting on different line from Transmitter65 Feedback Line Upstream of Feed- back, acting on different line from Transmitter______________________________________

The claims set forth hereinafter cover various ones of the several illustrated embodiments and various permutations and combinations of the illustrated embodiments as will appear therefrom.

Claims

1. A fluidic repeater system comprising:

transmitter means,

receiver means,

connector conduit means including first and second conduit means,

said first conduit means connecting said transmitter means to said receiver means, said first conduit means including two high pressure conduits,

source means for supplying fluid under pressure to said first conduit means, said source means including for each said high pressure conduit a fluid supply passage having an inlet and an outlet with a restriction therebetween whereby when said inlet is connected to a source of pressure fluid said outlet will provide a fluid supply having a drooping pressure versus rate of flow characteristic, said outlets being connected to the high pressure conduits;

said receiver means including load means and load feedback means,

said load means including responder means for producing mechanical movement and including a piston in cylinder connected to each said high pressure conduit for relative axial movement of the piston and cylinder in response to variation in the pressure in one of said high pressure conduits;

reservoir means including a reservoir of fluid at a lower pressure than said source,

said second conduit means interconnecting said reservoir means with said transmitter means and said receiver means, said second conduit means constituting low pressure conduit means,

said transmitter means serving for venting at least one of said high pressure conduits to said low pressure conduit means in accordance with the position of the transmitter means, thereby to vary the pressure in said high pressure conduit,

said transmitter being positionable over a range of positions including a first position of maximum venting and various positions in between said first and second positions to produce different amounts of movement of the responder means for each of the several positions of the transmitter means within said range of positions,

said load feedback means being responsive to movement of said load means for venting at least one of said high pressure conduits to said low pressure conduit means, and

fluid resistance means in said connector conduit means for balancing

(i) the fluid resistance between said source means and said reservoir means along a transmitter path extending through said transmitter means, excluding the resistance of said transmitter means, with

(ii) the fluid resistance between said source means and said reservoir means along a feedback path extending through said load feedback means, excluding the resistance of said load feedback means,

such that such fluid resistance along said transmitter path is approximately equal to such fluid resistance along said feedback path.

2. The fluidic repeater system of claim 1 wherein: said fluid resistance means includes a plurality of balancing conduits formed by portions of said first and second conduit means that constitute said transmitter path and said feedback path respectively, said balancing conduits connecting said transmitter means and said receiver means to said first and second fluid conduit means such that the total length of the path from said source means to said reservoir means through said load feedback means exclusive of the portion of such path through said feedback means is substantially equal to the total length of the path from said source means to said reservoir means through said transmitter means exclusive of the portion of the last-mentioned path through the transmitter means,

said balancing conduits having substantially identical and constant cross-sectional areas.

3. The fluidic repeater system of claim 2 wherein: each of said high pressure conduits included in said first conduit means extends separately all the way from the transmitter means to the receiver means, and said balancing conduits include a first and a second balancing conduit connecting said high pressure conduits separately to said transmitter means, a third and a fourth balancing conduit connecting said high pressure conduit separately to said feedback means, a fifth balancing conduit connecting said low pressure conduit to said transmitter means, and a sixth balancing conduit connecting said low pressure conduit to said feedback means.

4. The fluidic repeater system of claim 2 wherein: said receiver means includes an amplifier, said transmitter means controlling said load through said amplifier, said amplifier including amplifier feedback means for variably venting fluid from at least a portion of said first fluid conduit means to said second fluid conduit means, said receiver means further including variable restriction means for variably restricting flow from said amplifier feedback means to said second fluid conduit means.

5. The fluidic repeater system of claim 1 wherein: said fluid resistance means includes a plurality of balancing conduits comprising portions of said first and second conduit means that constitute said transmitter path and said feedback path respectively, said balancing conduits connecting said transmitter means and said receiver means to said first and second fluid conduit means such that the total fluid resistance of the load feedback path from said source means to said reservoir means through said load feedback means exclusive of the fluid resistance of the portion of the load feedback path within the feedback means is substantially equal to the total fluid resistance of the transmitter path from said source means to said reservoir menas through said transmitter means exclusive of the fluid resistance of the portion of the transmitter path within said transmitter means.

6. The fluidic repeater system of claim 5 wherein: said plurality of balancing conduits includes a first portion connecting said first and second fluid conduit means to said transmitter means and a second portion connecting said first and second fluid conduits to said load feedback means, the balancing conduits of said first portion having greater length and larger inside cross-sectional area than do the balancing conduits of said second portion.

7. The fluidic repeater system of claim 5 wherein: said plurality of balancing conduits includes a first portion connecting said first fluid conduit means to said transmitter means, a second portion connecting said second fluid conduit means to said transmitter means, a third portion connecting said first fluid conduit means to said load feedback means, and a fourth portion connecting said second fluid conduit means to said load feedback means,

the conduits of said first and fourth portions of said plurality of balancing conduits having substantially identical cross-sectional area and length, and the conduits of said second and third portions of said plurality of balancing conduits having substantially identical cross-sectional area and length.

8. The fluidic repeater system of claim 7 wherein: the cross-sectional areas of all of the balancing conduits are substantially identical and the length of the conduits of said first and fourth portions of said plurality of balancing conduits differs from the length of the conduits of said second and third portions of said plurality of balancing conduits.

9. The fluidic repeater system of claim 1 wherein: said fluid resistance means includes variable restrictor means for variably obstructing flow through at least a portion of said second fluid conduit means.

10. The fluidic repeater system of claim 9 wherein: said variable restrictor means includes at least one variable restrictor disposed between said reservoir connection means and said load feedback means.

11. The fluidic repeater system of claim 10 wherein: said second fluid conduit means includes two low pressure conduits connected to said load feedback means, said

said variable restrictor means includes a first variable restrictor obstructing one of said low pressure conduits at a point downstream of said load feedback means and a second variable restrictor for variably obstructing the other of said low pressure conduits at a point downstream of said load feedback means.

12. The fluidic repeater system of claim 11 wherein: said receiver includes an amplifier, said amplifier including a piston axially movable within a cylinder, and

said load feedback means includes grooves on the ends of said piston communicating with grooves in said cylinder, and

said amplifier includes output conduits and isolation means for isolating flow through said output conduits from flow through said load feedback means.

13. The fluidic repeater system of claim 12 wherein: said isolation means includes lands on said piston positioned between said output conduits and said grooves in said cylinder.

14. The fluidic repeater system of claim 10 wherein: said two high pressure conduits connect said transmitter means to said load feedback means,

said low pressure conduit is connected to said load feedback means, and

said variable restrictor variably obstructs flow through said low pressure conduit.

15. The fluidic repeater system of claim 14 wherein: each said high pressure conduits includes a variable restrictor positioned at a point between said source means and said transmitter means.

16. The fluidic repeater system of claim 9 wherein: said fluid resistance means further includes a fixed restrictor for obstructing flow through at least a portion of said second fluid conduit means.

17. The fluidic repeater system of claim 1 wherein: said fluid resistance means includes a fixed restrictor for obstructing flow through at least a portion of said second fluid conduit means.

18. The fluidic repeater of claim 1 wherein: said fluid resistance means includes restrictor means for obstructing flow through at least a portion of said first fluid conduit means.

19. The fluidic repeater system of claim 18 wherein: said receiver includes an amplifier and said first fluid conduit means includes an amplifier portion connected to said amplifier and a load feedback portion connected to said load feedback means, flow through said amplifier portion being separate from flow through said load feedback portion, and

said restrictor means variably restricts flow through said load feedback portion.

20. The fluidic repeater system of claim 19 wherein: said first fluid conduit means includes a high pressure conduit connected to said transmitter, to said amplifier portion, and to said load feedback portion.

21. The fluidic repeater system of claim 19 wherein: said amplifier includes a piston axially movably disposed in a cylinder and said amplifier portion of said first fluid conduit means includes an extension of said cylinder.

22. The fluidic repeater system of claim 19 wherein: said first and second high pressure conduits include a first high pressure conduit part connecting to said transmitter and a second high pressure conduit part connecting to said amplifier portion and said load feedback portion.

23. The fluidic repeater system of claim 19 wherein: said load feedback portion includes a first and a second load feedback conduit part, said amplifier portion includes a first and a second amplifier fluid passageway, and said variable restrictor means includes a first variable restrictor for variably obstructing flow through said first load feedback conduit part and a second variable restrictor for variably restricting flow through said second load feedback conduit part.

24. A fluidic repeater system comprising:

a source of fluid under pressure;

a first flow restrictor and a second fluid restrictor;

a first fluid passage connected to said source through said first fluid restrictor;

a second fluid passage connected to said source through said second fluid restrictor;

a reservoir of fluid having a pressure less than that of the fluid of said source;

transmitter means for variably venting both said first fluid passage and said second fluid passage to said reservoir in such a manner that one of said fluid passages can be vented by said transmitter means while the other of said fluid passages is not vented by said transmitter means; and

first responder means including a first piston in a cylinder for providing mechanical displacement of said first piston with respect to said cylinder in response to change in the differential of the pressure of the fluid in said first fluid passage and the pressure of the fluid in said second fluid passage,

said responder cylinder having a reduced diameter portion, a first normal diameter portion on one side of said reduced diameter portion, and a second normal diameter portion on the other side of said reduced diameter portion, said first fluid passage communicating with said first normal diameter portion and said second fluid passage communicating with said second normal diameter portion,

said first piston including a responder piston shaft disposed in said reduced diameter portion of said responder cylinder and extending at each end into said normal diameter portions and having responder piston bearing lands at each end of said responder piston shaft, said bearing lands slidingly and sealingly engaging said normal diameter portions of said responder cylinder,

the cylindrical surface of said reduced diameter portion of said responder cylinder having an outlet port at its axial center and a radial passageway connecting said outlet port to said reservoir, and

feedback means including axial variable depth grooves in said responder piston shaft for variably venting the fluid at either side of said reduced diameter portion of said first responder cylinder to said reservoir,

said radial passageway including a variable restrictor means for variably restricting flow through said radial passageway.

25. A fluidic repeater comprising:

a source of fluid under pressure;

a reservoir of fluid having pressure less than the fluid of said source;

first restrictor means for restricting the flow of fluid;

passage means for carrying fluid flow connected to said source through said first restrictor means, said passage means slightly restricting the flow of such fluid;

first venting means for variably venting fluid within said passage means to said reservoir, said first venting means being controlled by an external force;

responder means for producing mechanical displacement according to the pressure of fluid within said passage means;

second venting means for variably venting fluid within said passage means to said reservoir, said second venting means being controlled by the mechanical displacement produced by said responder means, the distance along said passage means between one of said venting means and said first restrictor means being less than that between the other of said venting means and said first restrictor means; and

second restrictor means connected between said one of said venting means and said reservoir for restricting the flow of fluid vented by said one of said venting means.

26. A fluidic repeater as recited in claim 25 wherein the amount of restriction of said second restrictor means is variable.

27. A fluidic repeater as recited in claim 26 wherein said one of said venting means is said second venting means.

28. A fluidic repeater system comprising:

source means for supplying fluid under pressure including fluid supply passage having an inlet and an outlet with a restriction therebetween whereby when said inlet is connected to a source of pressure fluid said outlet will provide a fluid supply having a drooping pressure versus rate of flow characteristic,

responder means for producing mechanical movement and including a piston in cylinder connected to said fluid supply outlet for relative axial movement of the piston and cylinder in response to variation in the pressure at said fluid supply outlet,

transmitter means for venting said fluid supply outlet to reservoir means including a reservoir of fluid at a lower pressure than said source, in accordance with the position of the transmitter means, said transmitter being positionable over a range of positions including a first position of maximum venting and a second position of minimum venting and various positions in between said first and second positions to produce different amounts of movement of the responder means for each of the several positions of the transmitter means within said range of positions,

said transmitter means including a fluid path from said fluid supply outlet to the said reservoir means, and including a first opening forming part of said fluid path and first obstructor means for varying the fluid flow through said opening, and

feedback means responsive to the magnitude of the movement of said responder means, without the necessity for the magnitude to be changing with time and independent of the previous duration of such movement, for venting the same said fluid supply outlet to such reservoir means,

said feedback means including a fluid path from said fluid supply outlet to such reservoir means and including a second opening forming part of said fluid path and second obstructor means for varying the fluid flow through said opening,

said fluid path of said feedback means and said fluid path of said transmitter means being separate paths at least to the extent that fluid flow through said second opening of the feedback means is in parallel with fluid flow through said first opening of the transmitter means with none of the fluid flowing through said first opening flowing through said second opening on its way to such reservoir and none of the fluid flowing through said second opening flowing through said first opening on its way to such reservoir,

venting of said fluid supply outlet by said transmitter means being at a rate dependent upon position of first obstructor means without regard to the position of said second obstructor means and venting of said fluid supply outlet by said feedback means being at a rate dependent upon the position of said second obstructor means without regard to the position of said first obstructor means,

fluid resistance means for balancing the fluid resistance between said source means and said reservoir means along a transmitter path extending through said transmitter means, excluding the resistance of said first opening of said transmitter means, with the fluid resistance between said source means and said reservoir means along a feedback path extending through said feedback means, excluding the resistance of said second opening of said feedback means,

such that such fluid resistance along said transmitter path is approximately equal to such fluid resistance along said feedback path.

29. The fluidic repeater system of claim 28 wherein said fluid paths of said transmitter means and feedback means include a high pressure conduit connected to said transmitter means and to said load feedback means, said fluid resistance means including variable restrictor obstructing flow through said high pressure conduit.

30. A fluidic repeater system comprising:

transmitter means,

receiver means,

connector conduit means including first and second conduit means,

said first conduit means connecting said transmitter means to said receiver means, said first conduit means including at least one high pressure conduit,

source means for supplying fluid under pressure to said first conduit means, said source means including for each said high pressure conduit a fluid supply passage having an inlet and an outlet with a restriction therebetween whereby when said inlet is connected to a source of pressure fluid said outlet will provide a fluid supply having a drooping pressure versus rate of flow characteristic, said outlet being connected to the high pressure conduit;

said receiver means including load means and load feedback means,

said load means including responder means for producing mechanical movement and including a piston in cylinder connected to each said high pressure conduit for relative axial movement of the piston and cylinder in response to variation in the pressure in said high pressure conduit,

reservoir means including a reservoir of fluid at a lower pressure than said source,

said second conduit means interconnecting said reservoir means with said transmitter means and said receiver means, said second conduit means constituting low pressure conduit means,

said transmitter means serving for venting at least one of said high pressure conduits to said low pressure conduit means in accordance with the position of the transmitter means, thereby to vary the pressure in said high pressure conduit,

said transmitter being positionable over a range of positions including a first position of maximum venting and various positions in between said first and second positions to produce different amounts of movement of the responder means for each of the several positions of the transmitter means within said range of positions,

said load feedback means being responsive to movement of said load means for venting at least one of said high pressure conduits to said low pressure conduit means, and

fluid resistance means in said connector conduit means for balancing

(i) the fluid resistance between said source means and said reservoir means along a transmitter path extending through said transmitter means, excluding the resistance of said transmitter means, with

(ii) the fluid resistance between said source means and said reservoir means along a feedback path extending through said load feedback means, excluding the resistance of said load feedback means,

such that such fluid resistance along said transmitter path is approximately equal to such fluid resistance along said feedback path.