US3716071A

US3716071A - Fluidic logic device

Info

Publication number: US3716071A
Application number: US00187431A
Authority: US
Inventors: W Passera
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 1970-10-09
Filing date: 1971-10-07
Publication date: 1973-02-13
Anticipated expiration: 1990-02-13
Also published as: FR2110330B1; FR2110330A1; IT938973B; DE2049612A1; JPS478565A; GB1329957A; CH530565A

Abstract

A pneumatically or hydraulically operated fluidic logic device wherein a housing defines a ring-shaped chamber which communicates with fluid-supplying and fluid-discharging first and second passages as well as with a third passage for admission of a control fluid stream at a variable pressure. An elastically deformable split ring is received in the chamber with freedom of radial movement to seal the first and second passages from each other in response to a rise of fluid pressure in the third passage. The third passage has one or more channels machined into the surface which surrounds or is surrounded by the chamber, and each of the first and second passages has one or more channels machined into the surface which is surrounded by or surrounds the chamber. The split ring can be expanded to seal the first and second passages from each other if the channels of these passages are provided in the surface which surrounds the chamber, and the split ring is caused to contract and to thereby seal the first and second passages from each other if the channels of the first and second passages are provided in the surface which is surrounded by the chamber.

Description

United States Patent Passera 1 Feb. 13, 1973 FLUIDIC LOGIC DEVICE [57] ABSTRACT [75] Inv Waller 8898 Stuttgart, Germany A pneumatically or hydraulically operated fluidic logic [731 Assigneez Robert Bosch GmbH Smttgart Gen device wherein a housing defines a ring-shaped many chamber which communicates with fluid-supplying and fluid-discharging first and second passages as well [22] Filed: Oct. 7, 1971 as with a third passage for admission of a control fluid stream at a variable pressure. An elastically deforma- [211 App! 187431 ble split ring is received in the chamber with freedom of radial movement to seal the first and second [30] Foreign Application Priority Data passages from each other in response to a rise of fluid Oct 970 German P 20 49 612 2 pressure in the third passage. The third passage has y one or more channels machined into the surface 52] U S Cl 137/594 251/6 1 which surrounds or is surrounded by the chamber, and

[ 1 7/117 each of the first and second passages has one or more Field 251/61 1 channels machined into the surface which is sur- [5 6] References Cited UNITED STATES PATENTS 3,057,594 10/1962 Allen ..251/61.1 3,176,714 4/1965 Smith et a] ..l37/608 x Primary Examiner-Henry T. Klinksiek Att0meyMichael S. Striker rounded by or surrounds the chamber. The split ring can be expanded to seal the first and second passages from each other if the channels of these passages are 20 Claims, 17 Drawing Figures SHEET 1 [1F 9 PATENTEDfEB 13 1915 wvewrm Walter PASSERA SHEET 8 BF 9 PATENTEI] FEB I 3 I973 OJ w FLUIDIC LOGIC DEVICE BACKGROUND OF THE INVENTION The present invention relates to fluidic devices, and more particularly to improvements in fluidic logic devices which can be operated by a hydraulic or pneumatic control fluid and employ one or more valve members which are confined in a housing and are movable between several positions to thereby vary fluid connections between a plurality of fluid paths in the housing. Still more particularly, the invention relates to improvements in fluidic logic devices of the type known as hydrosistors (a term which has been coined after transistor owing to a certain analogy between the functions and fields of utilization of transistors and hydrosistors) wherein variations in the pressure of fluid in one or more control lines effect controlled changes in the position or positions of one or more valve members so as to permit or prevent the flow of one or more controlled hydraulic or pneumatic fluid streams between one or more supply conduits and one or more discharge conduits.

Austrian Pat. No. 276,892 discloses a fluidic device wherein a housing defines a cylindrical chamber for reception of a plate-like or piston-like valve member which is movable axially with a considerable amount of clearance. The valve member seals a passage for admission of a control fluid stream at one axial end of the chamber from passages for supply and discharge of a controlled fluid at the other axial end of the chamber. When the pressure in the passage for control fluid rises, the valve member moves against a seat at the other axial end of the chamber and thereby seals the supply passage from the discharge passage. If the fluid pressure in the control passage decreases, the valve member moves away from the seat and allows the controlled fluid to flow between the supply and discharge passages. The pressure of fluid which is admitted by way of the supply passage then moves the valve member to a position in which it seals the control passage from the chamber. Such fluidic devices occupy a substantial amount of space.

U.S. Pat. No. 3,362,633 to Freeman discloses a fluidic device wherein the housing defines an elongated for a disk-shaped pill. The control passage communicates with one end of the slot, and the other end of the slot communicates with a supply port and a discharge port. When the fluid pressure in the control passage rises, the pill is shifted sideways to move against-a seatin the slot and to thereby seal the two ports from each. other. If the fluid pressure in the control passage decreases, the fluid pressure in the supply I port moves the pill away from the seat and the two ports are free to communicate with each other. The patent to Freeman further discloses a ring-shaped valve member which can be used as a substitute for the diskshaped pill. A drawback of such fluidic devices is that,

cover a substantial distance in order to free a sufficiently large portion of the slot so that the latter can permit the flow of a substantial quantity of fluid between the supply and discharge ports. Consequently, such fluidic devices cannot be used in apparatus wherein the flow of a controlled fluid between the supply and discharge ports must be established and/or terminated at frequent intervals and with minimal losses in time. The same holds true for the piston-like valve member in the fluidic device of the Austrian patent.

SUMMARY OF THE INVENTION An object of the invention is to provide a fluidic logic device wherein the housing can provide one or more paths for the flow of substantial quantities of a controlled hydraulic or gaseous fluid medium even though the mass of the movable part or parts is small and even though the movable part or parts are called upon to perform strokes of short length and duration.

Another object of the invention is to provide a fluidic logic device which is highly resistant to wear, shocks and other mechanical influences, which can be readily protected against penetration and is not appreciably affected by eventual presence of foreign matter, and which can stand substantial thermal stresses without any appreciable influence upon its performance.

A further object of the inventionis to provide a fluidic logic device which can be designed to act as an amplifier or as an AND-, NO- or OR-gate in a wide variety of hydraulic or pneumatic control system.

An additional object of the invention is to provide a fluidic logic device which can operate properly even though its parts need not be machined or otherwise shaped and/or assembled with a high degree of precision, which can stand long periods of frequent use, and

slot of rectangular cross section and with rounded ends I which can be used as a superior substitute for presently known fluidic logic devices.

A further object of the invention is to provide a negative or positive hydrosistor wherein the mass of the movable valve member or members is less than in presently known hydrosistors.

Still another object of the invention is to provide a system using one or more novel and improved fluidic logic devices wherein one or more power streams of controlled fluid can be selectively switched into different output paths by one or more control fluid streams.

The invention is embodied in a hydaulically and/or pneumatically operated fluidic logic device which comprises a housing preferably consisting of two or more separable parts in the form of laminates or the like and has at least one ring-shaped chamber and a plurality of passages communicating with the chamber and including a fluid-supplying first passage, a fluid-discharging second passage and a third passage for admission of a control fluid stream at a variable pressure, and an elastically deformable slotted annular valve member which resembles a split ring and is received in the chamber with freedom of radial expanding or contracting movement in response to pressure changes in the first and/or third passage to move to and from a sealing position in which it separates the first and second passages from each other. The power stream of fluid which is admitted by way of the first passage can enter the second passage when the pressure of the control fluid stream is such that the valve member moves from its sealing position.

The housing is provided with first seat means which can be formed by the concave surface or surfaces of one or more arcuate ribs surrounding the ring-shaped chamber, and with second seat means which may be formed by the convex surface or surfaces of one or more arcuate ribs which are surrounded by the chamber. The third passage communicates with the chamber in the region of one seat means and the first and second passages communicate with the chamber in the region of the other seat means. When the pressure of the control fluid stream rises sufficiently, the valve member is deformed (whereby the width of its slot either increases or decreases) and is moved into sealing engagement with the other seat means to thereby separate the first and second passages from each other.

The other seat means may surround the ring-shaped chamber; the valve member is then preferably received in the chamber in such prestressed condition that it normally bears against the other seat means, i.e., the valve member tends to expand. Inversely, if the other seat means is surrounded by the chamber, the valve memberis inserted in prestressed condition in such a way that it normally bears against the other seat means, i.e., the valve member tends to contract.

The novel features which are considered as characteristic of the invention are set forth in particular in the appended claims. The improved fluidic logic device itself, however, both as to its construction and its mode of operation, together with additional features and advantages thereof, will be best understood upon perusal of the following detailed description of certain specific embodiments with reference to the accompanying drawing.

BRIEF DESCRIPTION OF THE DRAWING FIG. 1 is a substantially central vertical sectional view of a fluidic logic device which constitutes a negative hydrosistor or NO-gate and is constructed in accordance with a first embodiment of the invention, the valve member being shown in a first position;

FIG. 2 illustrates a detail in the structure of FIG. I but with the valve member in a different (sealing) position; I I

FIG. 3 is a horizontal sectional view as seen in the direction of arrows from the line III-III of FIG. 1;

FIG. 4 is a diagram of the negative hydrosistor shown in FIGS. 1 to 3;

FIG. 5 is a substantially central vertical sectional view-of a second negative hydrosistor which constitutes a modification of the hydrosistor shown in FIGS. 1 to 3;

FIG. 6 is a horizontal sectional view taken in the direction of arrows as seen from the line VI--VI of FIG. 5;

FIG. 7 is a fragmentary substantially central vertical sectional view of a third negative hydrosistor which constitutes a slight modification of the hydrosistor shown in FIGS. 5 and 6;

FIG. 8 is, a fragmentary horizontal sectional view of the hydrosistor shown in FIG. 7;

FIG. 9 is a substantially central vertical sectional view of a composite hydrosistor which embodies the hydrosistors of FIGS. I-3 and 5-6 and is connected with a single control line;

FIG. 10 is a diagram of the composite hydrosistor shown in FIG. 9;

FIG. 11 is a substantially central vertical sectional view of a hydrosistor which can be utilized as an AND- gate;

FIG. 12 is a diagram of the AND-gate shown in FIG. 1 1;

FIG. 13 is a substantially central vertical sectional view of a hydrosistor which can be used as an OR-gate;

FIG. 14 is a diagram of the OR-gate shown in FIG. 13;

FIG. 15 is a substantially central vertical sectional view of a hydrosistor which can be utilized as an amplifier;

FIG. 16 is a diagram of the amplifier shown in FIG. 15; and

FIG. 17 is a substantially central vertical sectional view of a hydrosistor which is similar to the fluidic logic device shown in FIGS. 1-3 and is further provided with an electromagnetically operated valve which regulates the flow of the control fluid stream.

DESCRIPTION OF THE PREFERRED EMBODIMENTS FIGS. 1 to 3 illustrate the details of a first fluidic logic device of the type known as a negative hydrosistor or n-hydrosistor. The principle of operation of an nhydrosistor is illustrated in FIG. 4. Its housing is connected with a control line or conduit X for a stream of control fluid, a supply line or conduit P for a power stream of fluid and a discharge line or conduit Y for the power stream. The medium which is admitted by way of the line P and whose flow is controlled by the nhydrosistor may be a liquid or a gaseous fluid. If the fluid pressure in the control line X rises, the pressure in the discharge line Y disappears. If there is no pressure in the control line X, the discharge line Y contains fluid under pressure because the discharge line then receives fluid from the supply line P; if the fluid pressure in the control line X thereupon rises, the pressure of fluid in the discharge line Y disappears again because the latter is cut off or separated from the supply line P.

Referring to FIGS. 1 to 3 in detail, the n-hydrosistor therein shown comprises a housing which includes a first portion or base 1, a second portion or cover 3 and a third portion or side wall 33. The base 1 has a substantially centrally located recess or blind bore 2 including alarger-diameter section nearer to its open or outer end and a smaller-diameter section nearer to its closed or inner end. The cover 3 is secured to the base 1 by screws 4 or analogous fasteners and comprises a substantially centrally located projection or stem 5 which includes a larger-diameter portion received with small clearance in the larger-diameter section of the bore 2 and a smaller-diameter portion which extends with clearance into and defines a ring-shaped chamber or space 8 with the cylindrical internal surface surrounding the smaller-diameter section of the bore 2. The larger-diameter portion of the stem 5 has a circumferential groove 6 for a sealing element in the form of an O-ring 7 which engages the adjacent portion of the internal surface of the base 1 and seals the ring-shaped chamber 8 from the open end of the bore 2.

In accordance with a feature of the present invention, the chamber 8 receives a slotted radially expandible and contractible elastic annular valve member or shuttle 9 which resembles a split ring and may consist of a metallic or synthetic plastic material. The term annular is intended to embrace truly circular shapes as well as oval and like shapes which deviate from a truly circular form. The outer-diameter of the shuttle 9 (which is inserted in prestressed condition) is such that the external surface of the shuttle bears against the adjacent portion of the surface surrounding the chamber 8. The shuttle 9 is received in the chamber 8 with some freedom of axial movement. The n-hydrosistor of FIGS. 1 to 3 further comprises a device for holding the shuttle 9 against rotation in the chamber 8; such device comprises a pin or stud 10 which is mounted in the stem 5 (see FIG. 3) and extends radially outwardly through the axially parallel slot 9a of the shuttle and into an axially parallel recess 11 of the base 1. ln theillustrated embodiment, the width of the chamber 8, as considered in the radial direction of the stem 5, is about one-andhalf to three times the wall thickness of the shuttle 9.

The smaller-diameter portion of the stem 5 is provided with two arcuate peripheral grooves or

channels

12, 13 of finite length; these grooves or channels are interrupted in the region of the pin 10. The

channels

12, 13 are flanked by

ribs

14, 16 and are separated from each other by a median rib the latter may but need not establish a complete seal between the two channels when the internal surface of the shuttle 9 bears against the

ribs

14 and 16. The stem 5 is further provided with at least one transverse (diametrically extending) bore 17 whose ends communicate with the channel 13 and at least one transverse (diametrically extening) bore 18 whose ends communicate with the channel 12. The median portions of the bores 17, 18 communicate with an axially extending blind bore 19 which is in communication with a tapped socket or input port 20 for a threaded nipple (not shown) which is connected to one end of the control line X. The port 20, the

channels

12, 13 and the

bores

17, 18, 19 form -a passageway or passage which connects the control line X with the chamber 8 at the inner side of the shuttle 9, i.e., in the region of the ribs 'or seats 14-16.,

That portion of the internal surface of the base 1 which surrounds with clearance the

channels

12, 13 of the stem 5 is provided with arcuate grooves or

channels

22, 23, 24 of finite length. Each of these channels is interrupted in the region of the pin 10, the same as the

channels

12 and 13. The free ends of the annular shuttle 9 in the region of the slot 90 overlie the respective ends of the channels l2, l3 and

channels

22, 23, 24 to an extent which approximates the thickness of the

ribs

14, 15 and 16. The two

outer channels

22, 23 are respectively flanked by arcuate webs or ribs 27, 28 and the

channels

22, 24 and 23, 24 are respectively separated from each other by arcuate ribs or

webs

25, 26 which are provided in the base 1. The width of the median channel 24 approximates or equals twice the width of the channel 22 or 23 (as considered in the axial direction of the stem 5), and this median channel 24 communicates with a bore 31 which is machined into the base 1 and communicates with a tapped output port 35 provided in the aforementioned side wall 33 of the housing. The channel 24 constitutes with the port 35 and bore 31 a passage which connects the chamber 8 with the discharge line Y at the outer side of the shuttle 9, i.e., in the region of the ribs or seats 25-28. The

side wall 33 is secured to a flat outer surface of the base 1 by screws or analogous fasteners, not shown. The

channels

22 and 23 communicate with two bores 32 (one shown in FIG. 3) which are machined into the base 1 and communicate with a tapped input port 34 of the side wall 33. The input port 34 can receive a threaded nipple (not shown) at one end of the supply line P and the output port 35 receives a similar nipple at one end of the discharge line Y. The

channels

22, 23 constitute with the port 34 and bores 32 a passage which connects the line P with the chamber 8 at the outer side of the shuttle 9, i.e., in the region of the ribs or seats 25-28. The height of the bore 31 (as considered in the axial direction of the stem 5) equals or approximates the height of the channel 24, and the height of each of the two bores 32 equals or approximates the height of the

respective channel

22 or 23. The cross-sectional area of the bore 31 equals or approximates the cross-sectional area of the discharge line Y, and the combined cross-sectional area of the bores 32 equals or approximates the cross-sectional area of the supply line P.

- The depth of each of the

channels

22, 23 increases preferably steadily in a direction from the pin 10 toward the respective bore 32, and the depth of the channel 24 increases preferably steadily in adirection from the pin 10 toward the bore 31. This is clearly shown for the channel 22 in FIG. 3 of the drawing.

The operation of the n-hydrosistor shown in FIGS. 1 to 3 is as follows:

When the pressure of control fluid in the line X and the pressure of the power stream of fluid in the supply line P is zero, the valve member or shuttle 9 bears (due to its own elasticity) against the ribs or seats 25-28 of the base 1 whereby such ribs act as abutm'ents for the shuttle. This is shown in FIG. 1.

1f the pressure of a gaseous or liquid control fluid in the line X rises, the innate elasticity of the shuttle 9 (its tendency to expand) is assisted I by fluid pressure against its internal surface so that the external surface of the shuttle is pressed against the ribs or seats 25-28 with a greater force to thus insure a reliable sealing action between the channel 24 (discharge line Y) and the channels 22, 23 (supply line P). The bias of the external surfaceof the shuttle 9 upon the concave surfaces of the ribs 25-28 depends on fluid pressure in the control line X. The shuttle 9 completely seals the lines P and Y from the control line X and from each other. The width of the axially extending slot 9a in the shuttle 9 increases in response to deformation of the shuttle as a result of increasing fluid pressure in the channels 12,

The pressure of a hydraulic or pneumatic fluid in the supply line P can also be used to regulate the sealing action of the shuttle 9. Thus, if the fluid pressure in the supply line P rises to equal that in the control line X,

.the pressure at the inner side of the shuttle 9 equals the of the shuttle 9 is readily discernible in FlG. l or 2. Thus, when the fluid pressure in the supply line P equals that in the control line X, the shuttle 9 bears against the

ribs

25, 26 and thus prevents any flow of the power stream of fluid between the lines P and Y.

1f the fluid pressure in the control line X decreases below the fluid pressure in the supply line P to such an extent that the fluid pressure in the

channels

22, 23 can effect a deformation and resulting movement of the shuttle 9 away from the concave surfaces of the ribs 25-28 and toward the convex surfaces of the ribs 14-16, the supply line P is free to communicate with the-discharge line Y by way of the input port 34, bores 32,

channels

22, 23, chamber 8 at the outer side of the shuttle 9, channel 24, bore 31 and output port 35. Such communication takes place when the fluid pressure in the

channels

22, 23 overcomes the fluid pressure in the

channels

12, 13 as well as the innate tendencyof the shuttle 9 to expand into sealing engagement with the ribs 25-28. The force which the shuttle 9 produces due to its innate elasticity is relatively small so that, for all practical. purposes, the supply line P begins to communicate with the discharge line Y as soon as the fluid pressure in the

channels

22, 23 overcomes the fluid pressure in the

channels

12, 13. The deformation of shuttle 9 in a direction to allow communication between the lines P and Y is accelerated as soon as the external surface of the shuttle moves away from the concave surfaces of the ribs 2528 because the pressure in the channel 24 rises practically instantaneously so that the fluid pressure is felt by a larger portion of the external surface of the shuttle, namely, by the entire external surface. The fluid pressure against the external surface of the shuttle 9 is somewhat less than the initial pressure of fluid in the channels 22, 23 (prior to movement of the shuttle from sealing engagement with the ribs 25-28). However, and since the shuttle 9 is received in the chamber 8 with minimal axial play,

losses due to the flow of fluid along the arcuate longitudinal edge faces of the shuttle are negligible and, the internal surface of theshuttle moves into highly satisfactory sealing engagement with the ribs 14-16 practically without anyv delay. Upon completed opening of the hydrosistor, i.e., when the internal surface of the shuttle 9 bears against the convex surfaces of the ribs whereby the lines P and Y communicate with each other in such a way that the flow of fluid between these lines is practically unimpeded. The flow takes place at the outer side of the shuttle 9 whereby the fluid flows across the

intermediate webs

25, 26 to leave the

channels

22, 23 and to enter the channel 24 on its way into the discharge line Y through the bore 31 and output port 35.

If the shuttle 9 is to assume its flow blocking position, the fluid pressure in the control line X is increased whereby the shuttle is subjected to fluid pressure in the

channels

12, 13 and undergoes a change in shape due to its elasticity and also due to the action of forces resulting from the fluid flow. The latter action is due to the fact that the speed of fluid flow across the

ribs

25, 26 between the channel 24 and the

channels

22, 23 is greater than in the channels 22-24 so that the pressure at the concave surfaces of the

ribs

25, 26 is lower. Furthermore, and as a result of unavoidable flow losses, the pressure in channels 22-24 is lower than in the

channels

12, 13 which branch off upstream of the fluid admitting passages. Due to the pressure differential, there develops a force which acts against the internal surface of the shuttle 9 and tends to move it radially outwardly. Consequently, the shuttle is pressed toward the ribs 25-28, and such action is assisted by innate elasticity of the shuttle. The expansion of the shuttle is accelerated because, as the clearances between the external surface of the shuttle and the

ribs

25, 26 decrease, the speed of fluid flow across the

ribs

25, 26 increases with attendant drop in pressure. When the clearances between the shuttle 9 and the

ribs

25, 26 decrease to such a value that the viscosity of the flowing fluid prevails, the pressure in the channel 24 begins to drop very rapidly so that the shuttle abruptly terminates any further flow of fluid from the channels 22 23 (supply line P) to the channel 24 (discharge line Y).

By properly dimensioning the supply line P and the

channels

22, 23, one can insure that the difference between the pressures acting against the internal and external surfaces of the shuttle 9 will remain low. In such hydrosistors, the movement of the shuttle to its sealing position will take place mainly due to its elasticity. Depending on the desired speed of sealing action, the shuttle must be inserted in a more or less stressed condition or its thickness must be selected in such a way that it can produce a desired expanding force which urges its external surface into sealing engagement with the ribs 25-28.

The differential force can also be increased by resorting to a suitable throttle or flow restrictor, e.g., a constriction in the supply line P downstream of the point where the control line X branches off. Even a very slight throttling action upon the flowing fluid will suffice.

It is clear that the direction of fluid flow can be reversed, i.e., that the fluid can be admitted via port 35, how 31 and channel 24, and evacuated by way of

channels

22, 23, bores 32 and port 34. 1

An important advantage of the elastically. deformable slotted valve member or shuttle 9 is that it requires a minimum of deformation or radial contractionin the chamber 8 to establish a large path for the flow of substantial quantities of power fluid between the lines P and Y, not only in the chamber 8 proper but also in the fluid supplying and fluid discharging passages which connect the,chamber 8 with the lines P and Y. The seats furnished by the ribs 14-16 and 25-28 are preferably of cylindrical shape to further enhance the sealing action of the shuttle 9 in each of its two sealing positions, i.e., when the shuttle seals the chamber 8 from the channels 12-13 and when the shuttle seals the chamber 8 from the channels 22-24 while simultaneously separating the channel 24 from the channels 22,

Another important advantage of the ring-shaped chamber 8 and substantially annular shuttle 9 which resembles a split ring is that the fluid which flows through the chamber 8 between the lines P and Y is deflected much less than in pill-type fluidic devices. Still further, since the valve member is an annular body, its mass per unit length (as considered in the circumferential direction of the stem is very small, and the mass can be reduced still further by reducing the thickness of the shuttle. Such reduction in thickness of the shuttle is preferably accompanied by an increase in the number of ribs or analogous seats in a manner to be described in connection with FIGS. 7 and 8. The relatively small mass and relatively short strokes of the shuttle between its sealing positions of engagement with the ribs 14-16 or 25-28 render it possible to rapidly change the position of the shuttle in response to the application of relatively low control fluid pressures and to allow for frequent changes in the position of the shuttle with negligible wear. Since the extent of deformation of the shuttle 9 is relatively small, the magnitude of bending and other stresses during deformation of the shuttle is minimal and the wear on the housing surfaces which surround and are surrounded by the chamber 8 is negligible. Sincethe shuttle is elastic, it can readily compensate for manufacturing tolerances so that the seats furnished by the ribs 14-16 and 25-28 need not be machined or otherwise formed with a high degree of precision. Tolerances which are due to deviations from circular shape, conicity, deviations from an optimum diameter, absence of flat surfaces at the axial ends of the chamber 8 and/or others are readily and fully compensated for by deformability of the shuttle in response to the application of fluid pressure by the control fluid stream (line X) and/or power stream (line P). Still further, the deformability of the shuttle 9 renders it possible to fully compensate for substantial deformations which may arise as a result of relatively high mechanical and/or thermal stresses. Also, the wear on the seats around and within the chamber 8 can be accepted for long periods of time due to deformability of the slotted annular shuttle 9. It was found that the shuttle 9 is subject to automatic adjustment in its normal position as a result of progressing wear on the shuttle proper aswell as a result of wear on the seats furnished by the 'ribs' 14-16 and 25-28. The deformability of shuttle 9 further reduces the likelihood of faulty operation in response to penetration of solid particles or other foreign matter which might be entrained by the control fluid stream and/or by the stream ofpower fluid. Thus, the presence of a particle of dust or the like between the shuttle 9 and one of the ribs' 14-16 or 25-28 affects' the operation of the improved hydrosistor much less than the operation of a conventional fluidic'logic device wherein the valve member is a rigid body in the form of a pill, circumferentially complete ring, plate, piston or the like which must invariably be guided in precision-finished slots, bores, cylinder chambers or the like. The fluidic logic device of the present invention can be utilized as an output amplifier or as a control element (such as an OR-, NO- or AND- gate) whereby the intended purpose of the device depends .to a certain extent on its size. An amplifier type hydrosistor will be described in connection with FIG. 15, and hydrosistors which can be used as AND- gates and OR- gates will be respectively described in connection with FIGS. 11 and 13.

In theembodiment of FIGS. 5 and 6, the discharge line Y communicates with a tapped output port 46 in the cover 103 and the base 101 of the housing has two tapped

input ports

43, 53 which respectively communicate with the control line X and supply line P. The grooves or

channels

112, 113 are machined into or otherwise formed in the cylindrical surface surrounding the recess 102 of the base 101 and communicate with the input port 43 by means of two

bores

41, 42. The

channels

122, 123, 124 are machined into or otherwise formed in the cylindrical peripheral surface of the stem 105 which extends into the recess 102 and defines with the base 101 a ring-shaped chamber 108 for a slotted elastic annular valve member or shuttle 109. The latter is held against rotation by a radial pin 110 of the stem 105 and is inserted under an initial stress in such a way that it tends to. bear against the convex surfaces of the webs or

ribs

125, 126, 127, 128 on the stem 105. The ribs 114, 115,116 alternate with the channels 112,113 and are provided in the base 101. The passage which includes the medium channel 124 (which is wider than the channels 122, 123) and the port 46 and serves to connect the chamber 108 with the line Y further includes a transverse bore 44 and an axial bore 45, both provided in the stem 105 of the cover 103. The passage between the chamber 108 and the line P includes the

channels

122, 123, the input port 53, radial bores 48,

49, axially parallel bores 50, a circumferential groove 51 in the stem 105, and a bore 52 in the base 101. The bores 50 connect the bores 48, 49 with the groove 51. The passage which connects the control line X with the chamber 108 includes the port'43, the

bores

41, 42 and the

channels

112, 113. The reference character 104 denotes one of the screws which connect the cover 103 with the base 101.

The mode of operation of the hydrosistor of FIGS. 5-6 is analogous to that of the hydrosistor shown in FIGS. 1-3. The main difference is that the initial stressing of the shuttle 109 is such that it tends to bear against the ribs 125-128 of the stem 10s, i.e., that the shuttle 109 tends to contract. I

The heretofor described hydrosistors are designed for operation at relatively low fluid pressures, for example, up to l0 atmospheres superatmospheric pressure. For use at elevated pressures, for example, in the range of up to and in excess of 100 atmospheres superat-v mospheric pressure, it is necessary to provide a larger number of ribs and/or webs to properly prop the deformable shuttle at the side which is opposite to the side acted upon by fluid pressure. .One such hydrosistor is shown in FIGS. 7 and 8. This hydrosistor is generally similar to the device of FIGS. 5-6. The base 201 is formed with six channels 55 which communicate with the input port 243 for the control line X, and such channelsare flanked and separated from each other by seven arcuate ribs or seats 56. The stem 205 of the cover 203 has six channels including two median channels 58 which communicate with the output port 246 for the discharge line Y and two pairs of outer channels 57 which communicate with the input port 253 for the supply line P. The ribs 59 flank and separate the

channels

57, 58 from each other.

In order to reduce the losses at the axial ends of the elastic shuttle 209, the chamber 208 between the base 201 and stem 205 accommodates an arcuate insert 54 which is secured to the stem 205 by a radial pin 210. The insert 54 is received in the slot 209a of the shuttle 209 and holds the latter against rotation in the chamber 208. The two end faces of the insert 54 abut against the adjacent surfaces at the respective axial ends of the chamber 208 and this insert is installed between those portions of the surfaces on the base 201 and stem 205 which are free of channels. The length of the insert 54, as considered in the circumferential direction of the stem 205, is such that there remains a negligible clearance between the axially parallel end surfaces of the shuttle 209 (namely, the surfaces which flank the slot 209a of the shuttle) and the adjacent surfaces 54a, 54b of the insert. The surfaces 54a, 54b of the insert 54 are parallel with the respective end surfaces of the shuttle 209. If desired, the surfaces 54a, 54b may be of concave shape so as to be more accurately tracked by the end surfaces of the shuttle 209 when the latter undergoes deformation in response to the application of fluid pressure or as a result of its own resiliency.

FIG. 9 illustrates a twin or composite hydrosistor which is a combination of the devices shown in FIGS. 1-3 and 5-6. This composite hydrosistor is connected with a single control line X (see FIG. and with two discrete supply lines P1, P2 and two discrete discharge lines Y1, Y2. The housing of the hydrosistor of FIG. 9 defines two ring-shaped

chambers

60, 61 which respectively receive slotted annular'elastic valve members or shuttles 62, 63. The control line X is in communication with channels64, 65 which are machined into or otherwise formed in an intermediate housing portion 66. The base 301 has an input port which communicates with the pressure line P1 and with

channels

322, 323 provided in the cylindrical surface surrounding the outer chamber 61, and an output port which communicates with the discharge line Y1 and with a further channel 324 provided in the surface surrounding the outer chamber 61. The channels 64 are provided at the inner side of the shuttle 63.

The cover 303 has a stem 305 which is provided with an input port for the supply line P2 and an output port for the discharge line Y2. The supply line P2 communicates with channels 322', 323' and the discharge line Y2 communicates with a channel324 of the stem 305. The channels 65 are provided in the intermediate housing portion 66 at the outer side of the shuttle 62. In this embodiment of the hydrosistor, a change of fluid pressure in the control line X can establish or terminate communication between the lines P1, Y1 and P2, Y2 (see FIG. 10). The

housing portions

301, 66 cooperate substantially as the

housing portions

1, 3 of FIGS. l-3 and the

housing'portions

66, 303 cooperates substantially as the housing portions 101, 103 of FIGS. 56.'

FIG. 11 illustrates a composite hydrosistor which is a combination of the devices shown in FIGS. 1-3 and 56 and acts as an AND-gate. The diagram of this hydrosistor is shown in FIG. 12. The hydrosistor is connected with two control lines X1, X2, a single supply line P and a single discharge line Y. The fluid discharging channel 70 of the outer hydrosistor is connected with the supply channels 71 of the inner hydrosistor. The control line X2 communicates with the

channels

412, 413 at the inner side of the shuttle 309 in the outer hydrosistor and the control line X1 communicates with the channels 412', 413' at the outer side of the shuttle 309' in the inner hydrosistor. When the shuttles 309, 309' are moved to the illustrated open positions, the discharge line Y communicates with the aforementioned channels 71 of the inner hydrosistor and with the channel 70 of the outer hydrosistor.

The structure shown in FIGS. 13 and 14 constitutes an OR-gate. As indicated schematically in FIG. 14, this structure also comprises two hydrosistors and is connected with two control lines X1, X2, a supply line P and a discharge line Y. The supply line P communicates with the channels 74 of the inner hydrosistor and with the channels 75 of the outer hydrosistor. The discharge line Y communicates with the median channel 76 of the outer hydrosistor and the median channel 77 of the inner hydrosistor. The control line X1 communicates with the

channels

512, 513 at the inner side of the shuttle 509 in the outer hydrosistor, and the control line X2 communicates with the channels 512', 513' at the outer side of the shuttle 509' in the inner hydrosistor.

The heretofore described devices constitute discrete n-hydrosistors or combinations of n-hydrosistors. A positive hydrosistor (known as p-hydrosistor) is illustrated in FIG. 15, and its diagram is shown in FIG. 16. In contrast to an n-hydrosistor, the interior of the discharge line Y for a p-hydrosistor is respectively without pressure and under pressure simultaneously with the control line X. The p-hydrosistor of FIG. 13 is also a combination of two n-hydrosistor's including a first n-hydrosistor (shown in the left-hand part of FIG. 16) which is designed for conveying of relatively small quantities of a gaseous or liquid fluid and a second nhydrosistor (shown in the right-hand part of FIG. 16) which is designed for a large throughput of fluid. The discharge channel 80 of the smaller n-hydrosistor is in communication with the four control channels 81 of the large n-hydrosistor. The

supply channels

82, 83 of both n-hydrosistors are connected with a common supply line P. In order to allow for a drop of pressure in the discharge channel 80 of the smaller n-hydrosistor when the control channels 84 of the smaller n-hydrosistor. contain pressurized fluid, the channel 80 is in communication with a return conduit or line 0 by way of a bore 85, a compartment 86 and a flow restrictor 87 in a bore 88. The control line X is connected with the smaller n-hydrosistor; when the fluid pressure in the line X rises, the discharge channel 80 is sealed from the supply channels 83 by the shuttle 609 of the smaller nhydrosistor. This causes a drop of pressure in the bore because the latter is connected with the bore 88 and return line 0 by the flow restrictor 87. The pressure in the control channels 81 of the larger n-hydrosistor also decreases. Due to fluid pressure in the supply line P, which is effective in the channels 82, the shuttle 609 of the larger n-hydrosistor is biased against the ribs which flank the channels 81 to thus establish communication between the lines P and Y.

If the pressure in the control line X drops, the shuttle 609' of the smaller n-hydrosistor is biased against the ribs which flank the channels 84, this being due to fluid the supply line P. This insures that the interior of each control channel 81 in the larger n-hydrosistor is maintained under pressure. The shuttle 609 is deformed by undergoing expansion and thereby seals the discharge line Y from the supply line 1. The device of FIG. 15 acts as an amplifier.

In order to allow for proper regulation of fluid pressure in the control channels 712, 713 (FIG. 17), the stem 705 of the cover 703 can accommodate an electromagnetic valve 90. in order to reduce the switching time and to thus allow for high-frequency operation of the hydrosistor, the valve 90 is preferably placed as close to the shuttle 709 as possible. This reduces the length of the passageway between the valve and the chamber 708 with attendant reduction of the mass and inertia of fluid which is confined in such passageway. For the same reason, the movable parts of the valve 90 are preferably designed to perform very short strokes and are preferably of compact and lightweight construction. The cross-sectional area of the path for the fluid flow through the valve 90 can remain small because the volume of fluid which flows in the control line X in order to change the position of the shuttle 709 is relatively small.

The end face of the stem 705 of the cover 703 shown in FIG. 17 is provided with a blind bore or recess which receives the body 91 of the valve 90. The axial bore 719 of the stem 705 communicates with the control line X and registers with a bore 92 in the valve body 91. The bore 92 communicates with a compartment 93 in the valve body 91 and this compartment receives a spherical valve element 94 which is movablein the compartment 93 at right angles to the axis of the bore 719. The

control channels

712, 713 communicate with the compartment 93 by way ofa bore 95, and the compartment 93 further communicates with two relief bores 97, 98 by way of a bore 96.

The'bores

97, 98 are connected with the return line 0. The body 91 defines a valve seat which can be'engaged by the valve element 94 and surrounds that portion of the bore 96 which communicates with the compartment 93. The valve element 94 is connected with or forms part of an armature 100 of an electromagnet 100a which latter further includes a spring 99 serving to bias the armature 100 upwardly so that the valve element 94 seals the compartment 93 from the bore 92 when the ,electromagnet 100 a is deenergized. The space which accommodates the spring 99 is in permanent communication with the bore 92 by way of a bore 89 in the valve body 91 to insure an equalization of pressures.

When the electromagnet 100a is deenergized (see FIG. 17), the valve element 94 seals the control line X from the compartment 93 under the action of the spring 99. Thus, the pressure in the control channels I 712, 713 is zero and the shuttle 709 abuts against the

ribs

714, 715, 716. Therefore, the channel 724 communicates with the

channels

722, 723 to connect the supply line (not shown) with the discharge line (not shown). When the electromagnet 1000 is energized, the armature 100 stresses the spring 99 and moves the valve element 94 against the seat at the upper end of the bore 96. Thefluid pressure in the control line X is propagated via bore 719 and causes a rise of fluid pressure in the

channels

712, 713 which expands the shuttle 709 so that the latter seals the channel 724 from the

channels

722, 723 and thus interrupts the flow of fluid between the supply and discharge lines.

Without further analysis, the foregoing will so fully reveal the gist of the present invention that others can, by applying current knowledge, readily adapt it for various applications without omtiting features which fairly constitute essential characteristics of the generic and specific aspects of my contribution to the art and, therefore, such adaptations should and are intended to be comprehended within the meaning and range of equivalence of the claims.

What is claimed as new and desired to be protected by Letters Patent is set forth in the appended claims:

1. A hydraulically or pneumatically operated fluidic .logic device, comprising a housing having at least one ring-shaped chamber and a plurality of passages communicating with said chamber, said passages including a fluid-supplying first passage, a fluid-discharging second passage and a third passage for admission of a control fluid at a variable pressure; and a slotted elastically deformable annular valve member received in said chamber with freedom of radial movement and being movable in response to pressure changes in said third passage into and from a sealing position in which said member separates said first and second passages from each other.

2. A device as defined in claim 1, wherein said housing has first seat means surrounding said chamber and second seat means surrounded by said chamber, said third passage communicating with said chamber in the region of one of said seat means and said first and second passages communicating with said chamber in the region of the other of said seat means, said valve member being deformable in response to the pressureof control fluid in said third passage to sealingly engage said other seat means and to thus separate said first and second passages from each other.

3. A device as defined in claim 2, wherein said other seat means surrounds said chamber and said valve member is received in said chamber in prestressed condition so that it normally bears against said other seat means.

4. A device as defined in claim 2, wherein said other seat means is surrounded by said chamber and said valve member is received in .said chamber in prestress'ed condition so that it normally bears against said other seat means.

5. A device as defined in claim 1, wherein the width of said chamber, as considered in the radial direction thereof, is between one and one-half and three times the wall thickness of said valve member.

6. A device as defined in claim 1, wherein said valve 'memberis received in said chamber with minimal clearance, as considered in the axial direction of said chamber.

7. A device as defined in claim 1, wherein said housing has a first substantially cylindrical surface surrounding said chamber and a second substantially cylindrical surface surrounded by said chamber, said first and second passages comprising arcuate channel means provided in one of said surfaces and said third passage comprising arcuate channel means provided in the other of said surfaces.

8. A device as defined in claim 7, wherein said channel means are of finite length and said housing comprises rib means extending between said channel means of said first and second passages, said rib means constituting seat means for said valve member in said sealing position thereof.

9. A device as defined in claim 7, wherein said channel means of said first passage includes a plurality of channels which flank the channel means of said second and said housing comprising a ring-shaped portion.

disposed between said chambers, said third passage being provided in said ring-shaped portion and communicating with both said chambers and further comprising a second elastically deformable slotted annular valve member in said second chamber.

l3. A device as defined in claim 1, further comprising means provided in said housing for holding said valve member against rotation in said chamber.

14.,A device as defined in claim 13, wherein said means for holding comprises an insert fixedly received in said chamber in the slot of said valve member.

15. A device as defined in claim 14, wherein said valve member has a 'pair of end surfaces flanking said slot and said insert has a pair of complementary surfaces each closely adjacent to a different one of said end surfaces.

16. A device as defined in claim 15, wherein said complementary surfaces are at least substantially parallel to the respective end surfaces.

17. A device as defined in claim 14, wherein said complementary surfaces are concave surfaces.

18. A device as defined in claim 1, wherein said housing has a first substantially cylindrical surface surrounding said chamber and a second substantially cylindrical surface surrounded by said chamber, said first and second passages respectively having first and second channel means provided in one of said surfaces and said third passage comprising channel means provided in the other of said surfaces, at least one of said channel means having a plurality of arcuate channels and the respective passage further comprising means connecting said plurality of channels with each other.

19. A device as defined in claim 1, further comprising valve means actuatable to respectively connect and seal said third passage from a source of pressurized control fluid.

20. A device as defined in claim 1, wherein the width of the slot of said valve member changes in response to the deformation thereof.

Claims

1. A hydraulically or pneumatically operated fluidic logic device, comprising a housing having at least one ring-shaped chamber and a plurality of passages communicating with said chamber, said passages including a fluid-supplying first passage, a fluid-discharging second passage and a third passage for admission of a control fluid at a variable pressure; and a slotted elastically deformable annular valve member received in said chamber with freedom of radial movement and being movable in response to pressure changes in said third passage into and from a sealing position in which said member separates said first and second passages from each other.

2. A device as defined in claim 1, wherein said housing has first seat means surrounding said chamber and second seat means surrounded by said chamber, said third passage communicating with said chamber in the region of one of said seat means and said first and second passages communicating with said chamber in the region of the other of said seat means, said valve member being deformable in response to the pressure of control fluid in said third passage to sealingly engage said other seat means and to thus separate said first and second passages from each other.

4. A device as defined in claim 2, wherein said other seat means is surrounded by said chamber and said valve member is received in said chamber in prestressed condition so that it normally bears against said other seat means.

6. A device as defined in claim 1, wherein said valve member is received in said chamber with minimal clearance, as considered in the axial direction of said chamber.

9. A device as defined in claim 7, wherein said channel means of said first passage includes a plurality of channels which flank the channel means of said second passage.

10. A device as defined in claim 9, wherein said one surface surrounds said chamber.

11. A device as defined in claim 9, wherein said one surface is surrounded by said chamber.

12. A device as defined in claim 1, wherein said housing defines a second ring-shaped chamber, one of said chambers surrounding the other of said chambers and said housing comprising a ring-shaped portion disposed between said chambers, said third passage being provided in said ring-shaped portion and communicating with both said chambers and further comprising a second elastically deformable slotted annular valve member in said second chamber.

13. A device as defined in claim 1, further comprising means provided in said housing for holding said valve member against rotation in said chamber.

14. A device as defined in claim 13, wherein said means for holding comprises an insert fixedly received in said chamber in the slot of said valve member.

15. A device as defined in claim 14, wherein said valve member has a pair of end surfaces flanking said slot and said insert has a pair of complementary surfaces each closely adjacent to a different one of said end surfaces.