|Publication number||US3460436 A|
|Publication date||Aug 12, 1969|
|Filing date||May 24, 1967|
|Priority date||May 26, 1966|
|Publication number||US 3460436 A, US 3460436A, US-A-3460436, US3460436 A, US3460436A|
|Original Assignee||Jordan Kunik I, Takeda Michio|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (7), Referenced by (10), Classifications (8)|
|External Links: USPTO, USPTO Assignment, Espacenet|
Aug. 12, 1969 MICHIO TAKEDA I HYDRAULIC REGULATING SYSTEM AND APPARATUS 2 Sheets-Sheet 1 Filed May 24, 1967 \F R Aw WNW/7 /w u Q A Q w wf H mm & w 4. kw R NM \N A m lhw w \l INVENTOR Mcw/a 724 504 *i wow Aug. 12, 1969 MICHIO TAKEDA HYDRAULIC REGULATING SYSTEM AND APPARATUS Filed May 24, 1967 m y 4 2 7 w 3 4 5 M 4 p f m 4 a 4 m 7 1/ 6 w 8 2 i 3 7. /U y 1 w 2? 1 I; M T 3 5 4 5 3 W. 1 H 43 w 3 4 4 j 9 "W Z m fi 2 a 4 E, f 3 7 W 3 w 3 INVENTOR C/// 0 TA/(EDA 3,460,436 HYDRAULIC REGULATING SYSTEM AND APPARATUS Michio Takeda, Toyonaka, Japan, assignor of twenty percent to I. Jordan Kunik, New York, N.Y. Filed May 24, 1967, Ser. No. 641,021 Claims priority, application Japan, May 26, 1966, 41/ 33,907 Int. Cl. F1511 13/02, /00; (305d 16/00 US. Cl. 91-3 12 Claims ABSTRACT OF THE DISCLOSURE 2 Jet pipe hydraulic regulating system and apparatus wherein hydraulic fluid is transmitted to respective sides of a work piston as result of direct sensitive interaction between fluid jet stream and fluid receiving ports, thereby dispensing with intermediate four-way valve or the like.
BACKGROUND OF THE INVENTION Field of the invention This invention relates to hydraulic regulators wherein a pivotable fluid jet pipe, responsive to a deviation signal or the like, causes fluid pressure in a work cylinder to move a work piston in a suitable direction to counteract the deviation of work apparatus.
Description of the prior art Prior art hydraulic regulating systems are exemplified by US. Patent 3,282,283, which employs a jet pipe whose hydraulic stream moves a four-way valve which, in turn, operates a piston to produce a corrective movement to work apparatus which has deviated from a predetermined operating norm. Although regulating apparatus as disclosed by said patent performs quite satisfactorily in many cases, there are several drawbacks that tend to diminish optimum performance. For example, the fourway valve introduces sources of friction that reduce the sensitivity of the apparatus and as well as its efliciency. Furthermore, the nozzle of the jet pipe is spaced a considerable distance from the hydraulic fluid receiving apertures whereby an extensive pressure drop occurs. Because of this gap within which reflex hydraulic pressure is imposed upon the tip of the nozzle, there occurs a delay in response to the deviation signal input. Also, difliculty is encountered as a result of the fact that reverse reflex streams of fluid from the receiving holes do not impinge against all sides of the jet pipe nozzle in a completely uniform manner, thereby introducing errors into the system.
SUMMARY OF THE INVENTION The present invention comprises hydraulic regulating apparatus which dispenses with the intermediate structure of a four-way valve and provides for direct jet pipe action to produce movement of a controlled piston in response to corrective signals received by the jet pipe as a result of deviations of work apparatus from a predetermined operating norm.
According to the present invention, the function of socalled lands on the four-way valve in previous apparatus is now performed by lands that are formed on the end of the jet pipe itself. The jet pipe lands cooperate directly with fluid receiving ports that communicate without interruption with the respective sides of the work piston. The control lands are now located on the end of the jet pipe, and are in very close proximity to the respective fluid receiving ports. Since the jet pipe is mounted pivotally, the wall in which the fluid receiving ports are located and the respective lands on the jet pipe are all States Patent O arcuately formed with the same curvature concentric with the pivot axis of the jet pipe. The lands on the jet pipe are in very close proximity to the mouths of the respective receiving ports to the extent of establishing the very closest clearance that permits the movement of said jet pipe in response to deviation signals while, at the same time, fluid leakage is kept to a minimum. The jet pipe lands perform the function of valves for their respective fluid receiving ports in the stationary wall of the apparatus.
In the device of the present invention, the smooth and light movement of the jet pipe is realized without the frictional drawbacks that are experienced with the fourway valve of the prior art. Notwithstanding the elimination of the prior art four-way valve, the excellent dynamic functions of such a valve are now performed by the unique and improved jet pipe structure of the present invention where control lands are formed on the face of said pipe. The two lands on the jet pipe are substantially equal in width to that of the two receiving ports provided on a fixed wall communicating with a work cylinder. Thus, the pivotable jet pipe not only performs its function of projecting hydraulic fluid into receiving ports, but also it performs the function of the eliminated four-way valve while achieving the superior linear dynamic characteristics of the latter.
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a diagrammatic top view of the apparatus of the present invention, some parts being shown broken away or in section, and some parts being omitted, said view being taken approximately on line 11 of FIG. 2;
FIG. 2 is a side view of a portion of the apparatus in FIG. 1, taken approximately on line 22 of FIG. 1;
FIG. 3 is a representation of an elevation of the fixed wall with its fluid receiving ports and of an end view of the jet pipe with its fluid jet ports, said views being spaced apart for illustrative purposes;
FIG. 4 is illustrative of the views of FIG. 3 superimposed one over the other when the jet pipe is in its central null position;
FIG. 5 shows a portion of the apparatus of FIG. 1 where the jet pipe has been pivotally shifted to the left;
FIG. 6 diagrammatically shows the position of the jet pipe ports relative to the fixed wall receiving ports when the jet pipe is in the position shown in FIG. 5;
FIG. 7 shows a portion of the apparatus of FIG. 1 where the jet pipe has been pivotally shifted to the right;
FIG. 8 diagrammatically shows the positions of the jet pipe ports relative to the fixed wall receiving ports when the jet pipe is in the position shown in FIG. 7;
FIG. 9 shows a piston speed curve of the present apparatus in relation to the magnitude of the deviation signal input; and
FIG. 10 is a fragmentary view of an alternative embodiment of the invention herein.
DESCRIPTION OF THE PREFERRED EMBODIMENTS The drawings herein are intended to disclose the operating principles of the present invention and, hence, are not intended to be drawn to scale. Also, the drawings omit structures which are well known to the art and which are not necessary for the elucidation of the invention.
FIGS. 1 and 2 show the basic components of the invention which include a pivotable jet pipe 11, which has a longitudinal bore 12, the rear end of which communicates with a perpendicular channel 13 in a rotatable shaft 14 formed integrally with said pipe 11.
The lower end 16 of shaft 14 is mounted in the inner race 17 of a ball bearing whose outer race 18 is secured fast in a suitable stationary base 19.
The upper end of shaft 14 rotates against an apertured thrust bearing 21 or the like mounted in a recess 22 within the mouth of an inlet pipe 23. Inlet pipe 23 has an inlet channel 24 which communicates through the central aperture in bearing 21 with channel 13. Fluid under pressure is supplied from a suitable source schematically represented as S, through inlet channel 24, through channel 13, and thence through bore 12 to provide the continuous hydraulic jet streams that are projected by the forward end of jet pipe 11.
The forward end 26 of jet pipe 11 is widened to contain a transverse channel 27 with which bore 12 communicates. The respective ends of transverse channel 27 terminate in spaced apart jet ports 28 and 29, the inner edges of which are separated by a land 31. Those portions of the forward end face 32 of jet pipe extending outwardly and laterally from ports 28 and 29 are formed as lands 33 and 34, respectively, whose functions will be described hereinafter. See FIG. 3. The end face 32 of jet pipe 11 including lands 31, 33 and 34, is arcuate in shape, the curvature thereof being concentric with the pivoting axis of shaft 14.
Located opposite the outer free end of jet pipe 11 is a stationary fixed wall 36 having a face plate 37 which is either integrally formed with or is attached by suitable means to wall 36. In the embodiment shown in FIGS. 1 and 2, the exposed surface 38 of plate 37 is arcuate in shape, the curvature thereof being concentric with the pivoting axis of shaft 14 and, of course, having the same curvature as end face 32 of jet pipe 11.
Face plate 37 has a pair of spaced apart receiving ports 41 and 42 which communicate with outlet ports 43 and 44, respectively, in wall 36.
A work cylinder 46 which is operated by the control device herein contains a reciprocable work piston 47 whose shaft 48 extends through a wall of said cylinder and is connected to work apparatus, diagrammatically represented as A, which is comparable to that disclosed in US. Patent 3,282,283. Ports 43 and 44 are connected to cylinder 46 in respective locations on opposite sides of piston 47 by way of pipes 51 and 52, respectively.
Integrally formed with or suitably connected by liquid tight means to face plate 37 is a box-like structure comprising spaced apart end walls 53 and 54, a floor 56, a roof 57, and a rear wall 58. Rear wall 58 has an aperture 59' through which the free portion of jet pipe extends. Floor 56 has a pair of spaced apart drain holes 61 for removal of overflow hydraulic fluid. Wall 58 may be provided with inner surface curvatures 63 in order to guide fluid streams flowing from surface 38 of face plate 37 and along walls 53 and 54 into drain holes 61.
Feedback deviation signals from work apparatus A controlled by the present device are transmitted by means X well known in the art to a signal receiving system 64, said system being arranged to transmit a corrective movement to jet pipe 11 by solenoid means or the like by way of a suitable linkage as exemplified by rod 65 or the like connected to ring 66 or the like mounted intermediate the ends of jet pipe 11. Reference may be had to US. Patent 3,282,283 which discloses a typical deviation signal input system for controlling the movement of a jet pipe as may be incorporated into system 64. The deviation signal may be sensed by air pressure, back pressure from a micrometer system, electric or electronic means.
A null position for jet pipe 11 is established by rotatable screw 67 mounted in a stationary frame 68, the inner end of said screw adjustably determining the location of a circular cap 69 movable within a tube 71 mounted on frame 68. Captive within cap 69 is one end of spring 72, the other end of which is anchored on a boss 73 connected to ring 66 or to pipe 11. The tension of spring 72 is adjusted initially under the condition when the signal input to system 64 indicates that no deviation is manifested by the controlled work apparatus so that jet pipe 11 is located in a null position where its jet ports 28 and 29 are located in a central position between receiving ports 41 and 42, as shown diagrammatically in FIG. 4. Depending upon the deviation signal received by system 64, jet pipe 11 is moved thereby either to the left as shown in FIGS. 5 and 6, or to the right as shown in FIGS. 7 and 8.
In one embodiment of the present invention, jet ports 28 and 29 are rectangular or square in shape while receiving ports 41 and 42 are triangular in shape, the latter with one of their respective apices directed toward each other in a line parallel with the plane described by the center of the free end of jet pipe 11. let ports 28 and 29 and receiving ports 41 and 42 are arrayed in respective positions where the former move in a line parallel to the alignment of the latter. Surface 38 of plate 37 and end face 32 of jet pipe 11 are accurately finished with the same concentric curvature so that there is an even clearance therebetween during all pivoted positions of jet pipe 11. The distance between stationary plate surface 38 and jet pipe end face 32 is of the very closest clearance that permits movement of jet pipe 11 and which minimizes fluid leakage and enhances efficiency of operation.
When jet pipe 11 is in the neutral central or null position, as indicated in FIGS. 1, 2 and 4, lands 31, 33 and 34 of jet pipe end face 32 are located opposite plate surface 38 so as the block off receiving ports 41 and 42. This blocking is comparable in function to that of the lands on a four-way spool valve operating in a control system as disclosed, for example, in US. Patent 3,282,283.
For most effective performance of the device herein, lands 33 and 34 and receiving ports 41 and 42 should be dimensioned so that their respective widths are substantially equal. Thus, in the null position of jet pipe 11, a static hydraulic state is maintained on both sides of piston 47 in cylinder 46 in the condition of work apparatus A controlled by said piston operating in a desired predetermined manner.
OPERATION When work apparatus A controlled by the device herein deviates in its operation from a predetermined or desired norm, the deviation signal received by system 64 is translated by suitable means such as solenoids or the like into mechanical movement operating by way of rod to move jet pipe 11 pivotally in either left or right directions in accordance with corresponding directional deviations of said controlled apparatus. As shown in FIG. 5, a deviation signal has caused jet pipe 11 to be moved to the left whereby receiving port 41 is opened to receive the thrust of hydraulic jet fluid from jet port 28, as a result of which hydraulic pressure is increased on the left side of piston 47 to cause the latter to move to the right. Since receiving port 42 has become unobstructed, piston 47 is capable of moving to the right since hydraulic fluid from cylinder 46 to the right of said piston is permitted to flow back through receiving port 42 into the overflow box. The corrective movement of piston 47 continues until the controlled work apparatus A reaches its predetermined normal operating condition at which time the signal sensing system associated with said work apparatus causes signal receiving system 64 to restore jet pipe 11 to its central neutral position as shown in FIG. 1. Cybernetic or feedback signal systems are well known in the art and they are typified by the apparatus shown, for example, in U.S. Patent 3,282,283.
FIGS. 7 and 8 indicate the comparable operation of jet pipe 11 when caused to move pivotally toward the right whereby piston 47 is caused to move to the left in order to produce a corrective movement for controlled work apparatus A that has deviated from its predetermined operating norm.
Although FIGS. 5, 6, 7, and 8 show jet pipe 11 in respective extreme deviated positions, it is understood that in many, if not most cases, the angular deviation of jet pipe 11 will be somewhat less than illustrated since the corrective action upon piston 47 will take place and be completed before jet pipe 11 has swung to either of its extreme deflected positions.
Although receiving ports 41 and 42 are illustrated in FIGS. 3, 6 and 8 as being triangular in shape, thereby producing satisfactory operation of the device herein, it is understood that in other embodiments said ports may be formed in other shapes such as ellipses, rectangles, circles, or the like. The particular shapes of said ports can be empirically arrived at for obtaining the most ideal piston speed curve.
In an embodiment of the present invention employing receiving ports 41 and 42 shaped triangularly as shown in FIGS. 3, 6 and 8, there is achieved a controlled condition where the piston speed in the zone near the target zero point is very low, thereby reducing the magnitude of the piston inertia whereby the latter moves smoothly and stops firmly, precisely, and accurately at the target point without any appreciable oscillation or hunting, and without any shock effect. A typical piston speed curve is shown in FIG. 9.
In some embodiments of the present invention, it is possible to provide a jet pipe which continuously projects a single hydraulic jet stream into either of the receiving ports 41 and 42. A shown in FIG. 10, jet pipe 75, having a central bore 76, and which is mounted in a manner similar to jet pipe 11, is provided with a single jet port 77 which is capable of projecting hydraulic fluid under pressure into either receiving port 41 or 42. In this embodiment, the free end of jet pipe 75 has a sufiicient thickness surrounding the jet port 77 so as to provide lands 78 and 79 which completely cover receiving ports 41 and 42, respectively, when pipe 75 is in its central neutral location. Thus, when jet pipe 75 is moved in either direction, hydraulic fluid is projected selectively into either receiving port 41 or 42 in the same manner as described hereinbefore, thereby producing the same corrective control function as is produced by jet pipe 1-1. Lands 78 and 79 are shaped to have the same curvature as face 38 of plate 37, both of said curvatures being concentric with the pivoting axis of jet pipe 75. Lands 78 and 79 are dimensioned to be substantially equal in width with receiving ports 41 and 42 so that when said jet pipe is angularly deflected in any degree, the hydraulic pressure is increased on one side of piston 47 and simultaneously decreased on the other side thereof. Here, also, the distance between stationary plate surface 38 and the surfaces of lands 78 and 79 is of the closet clearance that permits movement of jet pipe 75 and which minimizes fluid leakage and enhances efiiciency of operation.
The dimensions of lands 78 and 79 are determined so that the movement of jet pipe 75 in either direction will cause hydraulic fluid to be projected into one of the receiving ports 41 or 42 while hydraulic fluid is permitted to flow from the other of said receiving ports into the overflow box and ultimately into drain hole 61.
In all of the embodiments herein, the lands on the forward end of the jet pipes are dimensioned and spaced relative to each other and to receiving ports 41 and 42 whereby the deflection in either direction of the jet pipe simultaneously increases hydraulic pressure on one side of piston 47 and reduces hydraulic pressure on the other side of said piston.
The preferred forms of the invention have been disclosed herein as providing for concentric curvatures of both the receiving aperture wall and of the land faces on the free end of the jet pipes, and wherein said respective concentric surfaces are very close to one another in order to achieve the desired high efficiency performance. It is understood, however, that where lower efiiciency would be satisfactory in some applications, the face 38 of wall 37 may be arranged to be perpendicular to the central line of the jet pipe when the latter is situated in its central, neutral position.
1. Hydraulic regulating apparatus comprising a stationary wall, first and second spaced apart fluid receiving ports in said wall, a jet pipe pivotally mounted opposite said wall, the free end of said jet pipe being movable in proximity to said wall, port means on the end of said jet pipe for projecting hydraulic fluid selectively into either one of said receiving ports, first valve means on said free end of said jet pipe cooperating with said first receiving port and second valve means on the free end of said jet pipe cooperating with said second receiving port, said first and second valve means closing said respective first and second receiving ports when said jet pipe is in its normal central, neutral position, the movement of said jet pipe in either direction causing both valve means to open both receiving ports and causing the hydraulic stream from the jet pipe to increase the hydraulic pressure in one of said receiving ports while hydraulic pressure is reduced in the other of said receiving ports.
2. Apparatus according to claim '1 and further comprising a work cylinder, a work piston movable reciprocably in said cylinder, means connecting said first receiving port directly to the interior of said cylinder on one side of said piston, and means connecting said second receiving port directly to the interior of said cylinder on the other side of said piston.
3. Apparatus according to claim 1 wherein said wall is arcuate in shape and said first and second valve means on said jet pipe are arcuate in shape, the curvature of said wall and of said first and second valve means being concentric with the pivot axis of said jet pipe.
4. Apparatus according to claim 3 wherein the distance between the arcuate surface of said wall and the arcuate surfaces of said valve means is of the closest tolerance to permit movement of said jet pipe relative to said wall with a minimum of fluid leakage.
5. Apparatus according to claim 1 wherein the respective widths of said receiving ports and of said valve means are substantially equal.
6. Apparatus according to claim 1 wherein said receiving ports are triangular in shape with an apex of one of said ports being directed toward and aligned with an apex of the other receiving port in a line parallel to the plane described by the movement of the center of the free end of said jet pipe.
7. Apparatus according to claim 1 and further comprising signal receiving means connected to said jet pipe responsive to deviation of a work apparatus in either of two directions from a predetermined operating norm to cause said jet pipe to move pivotally in a corresponding direction for projecting fluid into a corresponding receiving port to increase hydraulic pressure therein while hydraulic pressure is reduced in said second receiving port.
8. Apparatus according to claim 1 and further comprising a work cylinder, a work piston movable reciprocably in said cylinder, means connecting said first receiving port directly to the interior of said cylinder on one side of said piston, means connecting said second receiving port directly to the interior of said cylinder on the other side of said piston, work apparatus connected to said piston, and signal receiving means connected between said work apparatus and said jet pipe and responsive to deviation of said work apparatus in either of two directions from a predetermined operating norm to cause said jet pipe to move pivotally in a corresponding direction for increasing hydraulic pressure in one of said receiving ports while the hydraulic pressure in the other of said receiving ports is reduced.
9. Hydraulic regulating apparatus comprising a work cylinder, a work piston movable reciprocably in said cylinder, a stationary wall, first and second spaced apart fluid receiving ports in said wall, said first port connected to said cylinder on one side of said piston, said second port connected to said cylinder on the other side of said piston, a jet pipe piovtally mounted opposite said Wall, the
free end of said jet pipe being movable in proximity to said wall, port means on the end of said jet pipe for projecting hydraulic fluid selectively into either one of said receiving ports, a first land on one side of said jet port means, a second land on the other side of said jet port means, said first land substantially closing said first receiving port and said second land substantially closing said second receiving port when said jet pipe is located in a neutral, central position.
10. Apparatus according to claim 9 wherein said stationary wall in the location of said fluid receiving apparatus is arcuately formed and said free end of said pipe and said first and second lands are arcuately formed, both the curvature of said wall and of said lands being similarly concentric with the pivot axis of said jet pipe.
11. Apparatus according to claim 10 wherein the distance between the arcuate surface of said wall and the arcuate surface of said lands is of the closest clearance to permit movement of said jet pipe relative to said wall with a minimum of fluid leakage.
12. Hydraulic regulating apparatus comprising a work cylinder, a work piston movable reciprocably in said cylinder, a stationary wall, first and second spaced apart fluid receiving ports in said wall, said first port connected to said cylinder on one side of said piston, said second port connected to said cylinder on the other side of said piston, a jet pipe pivotally mounted opposite said Wall, the free end of said jet pipe being movable in proximity to said wall, port means on the end of said jet pipe for projecting hydraulic fluid selectively into either one of said receiving ports, first valve means on the end of said jet pipe cooperating with said first fluid receiving port and second valve means on said jet pipe cooperating with said second fluid receiving port, said first and second valve means substantially closing the respective first and second receiving ports when said jet pipe is located in a neutral, central position.
References Cited UNITED STATES PATENTS 1,776,817 9/1930 Mugler 9l3 2,904,057 9/ 1959 Callender et al. 9 l3 2,990,839 7/1961 Ray 137-83 3,081,787 3/1963 Metllendyk l37-83 3,347,253 10/1967 Moosmann l3783 FOREIGN PATENTS 695,260 9/1930 France. 1,092,710 1/ 1957 Germany.
PAUL E. MASLOUSKY, Primary Examiner US. Cl. X.R.
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|EP2980417A1 *||Jun 30, 2015||Feb 3, 2016||Zodiac Hydraulics||Dual mobile assembly servovalve|
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|U.S. Classification||91/3, 91/387, 137/83, 91/390|
|International Classification||F15C3/00, F15C3/12|