US2880706A

US2880706A - Servo-motor having chatter eliminating means

Info

Publication number: US2880706A
Application number: US612544A
Authority: US
Inventors: Price Earl Robert
Original assignee: Bendix Aviation Corp
Current assignee: Bendix Aviation Corp
Priority date: 1956-09-27
Filing date: 1956-09-27
Publication date: 1959-04-07
Anticipated expiration: 1976-04-07

Description

April 7, 1959 E. R. PRICE 2,880,706

SERVO-MOTOR HAVING CHATTER ELIMINATING MEANS Filed Sept. 27, 1956 [v] III F4 United States Patent SERVO-MOTOR HAVING 'CHATTER ELIMINATIN G MEANS Earl Robert Price, South Bend, Ind., assignor to Bendix Aviation Corporation, South Bend, Ind., a corporation of Delaware Application September '27, 1956, Serial No. 612,544

8 Claims. (Cl. 121-41) The present invention relates to fluid pressure control systems; and more particularly to means for controlling icc cylinder. A vacuum tight seal D capable of accommodating a slight amount of lateral movement, and similarly constructed to that described in application 559,556, now Patent No. 2,829,625, is employed between the push rod C and lthe end wall 10; and a curtain type diaphragm 12 is clamped between the piston B and the open end of i the cylinder A to provide an internal vacuum tight power chatter in pneumatic control valves for tluid pressure servo-motors and the like.

In fluid pressure control systems employing valving of comparatively large capacity for controlling devices which are quite sensitive to pressure, control valve chatter is often encountered. This is particularly true of uid pressure servo-motors of the type employing diaphragms as their movable walls-particularly where the device driven by the diaphragm exerts reactive forces which are largely reversible, and where considerable mass is carried by the diaphragm.

An object of the present invention is the provision of a new and improved control system of the above mentioned type which will substantially eliminate chatter of its control valve without materially reducing the inherent responsiveness of the system.

Another object of the invention is the provision of new and improved means for preventing chatter in control valves, which means is simple in design, rugged in con struction and eflicient in its operation.

A further object of the invention is the'provision of a l new and improved control system for a fluid pressure servo-motor and the like, and comprising a control valve for regulating uid ow communication with the servomotor, and a throttle or back-pressure valve of relatively large capacity in series flow circuit with the control valve and adapted to provide a restriction to the tluid ow as the ow rate through the control valve approaches zero. Further objects and advantages will become appa-rent to those skilled in the art to which the invention relates from the followingdescription of the preferred embodiment described with reference to the accompanying drawing forming a part of this specification, and in which:

Figure l is a cross sectional view of a vacuum powered iluid pressure servo-motor adapted to operate the brakes of an automotive vehicle, and embodying principles of the present invention;

Figure 2 is an enlarged isometric view of a part of the device shown in Figure 1; and

Figure 3 is a fragmentary view showing a second erna diaphragm type of sealing arrangement between its vpiston and cylinder walls while the Hupp device uses a The instant device generally comprises a sliding seal. cup shaped cylinder A having a piston B made from a sheet metal stamping located adjacent the open end of the cylinder, and provided with a tubular force transmitting member or .push rod C extending through an opening in the closed end wall 10 of the cup-shaped chamber 14.

The internal chamber 16 of the tubular push rod C forms part of a large valve chamber 18 that includes an enlarged opening in the piston B, and the central opening of an axially aligned tubular boss 20 bolted to the outer face of the piston B. The boss 20 is spaced apart from the external face of the piston B by a foraminous spacer member 22 to provide an annular atmospheric chamber 24 which surrounds the valve chamber and which is adapted to be closed off from the inner valve chamber 18 by an annular valve closure member 26. One end of the closure member 26 is sealed to the boss 20 by an annular diaphragm 28, and the other end of the closure member 26 ends in a flange 30 which normally abuts an annular atmospheric valve seat 32 in the opposite radial wall of the atmospheric chamber 24 to separate the atmospheric chamber 24 from the inner valve chamber 18. A movable poppet member 34 is positioned radially inwardly of the atmospheric valve seat 32, and is adapted for sealing engagement with the flange 30 so as to be capable of isolating portions of the axially extending valve chamber 18 falling on opposite sides of the flange 30. l`

The poppet member 34 is adapted to be moved by a push rod 36 extending through the tubular force transmitting member C to a point outside of the servo-motor; and a diaphragm 38 is positioned between the push rod 36 and the outer` end of the tubular force transmitting member C to 'seal oli this end of the valve chamber 18. The opposite end of the valve chamber 18 as formed by the tubular boss 20 is also closed 01T by a diaphragm 40, and a thrust rod 42 is positioned between the diaphragm 40 and the poppet member 34 to provide a valve balancing effect which will be more completely understood by referring to application 559,556, now Patent No. 2,829,- 625. The portion of the valve chamber 18 communicating with the tubular push rod C (right-hand portion 44 as seen in the drawing) communicates with the power chamber 14 of the servo-motor by means of passage- Way 46.

Vacuum is introduced to the opposite portion 48 of the Valve chamber 18 (left-hand portion as seen in the drawing) by means of vacuum connection 50;l and operation of the servo-motor is controlled by axialv movement of the push rod 36, as is more fully explained in the above referred to application.

The fluid pressure motor above described is intended to be used to operate the master cylinder of an automotive hydraulic braking system. It is a property of such systems thatmovement of the master cylinders iluid displacement member by the servo-motor is generally reversible; and that the fluid displacement member will return the servomotors piston when the force applied by the piston is relaxed. The combined effect of very sensitive valving and a frictionless power piston, when used to actuate generally reversible driven devices, produce control valve chatter which is most diicult to control.

y According to principles of the present invention, means are provided which successfully eliminate control valve chatter in this most diilcult application. The chatter eliminating means G shown in the drawing is positioned in the iluid flow stream which is controlled by the servomotors control valve during actuation of the motor. The servo-motor shown in the drawing is an atmospheric suspended unit that is actuated by communicating vacuum to its internal power chamber 14. During actuation, therefore, the control valve of the servo-motor throttles ow out of the power chamber into the vacuum supply line for the unit. The chatter eliminating means G shown in the drawing is positioned on the vacuum supply side of the motors control valve E and generally comprises a valve closure member 52 lightly biased by a coil spring 54 against a valve seat 56 in a manner as to lightly oppose iiow through the system. The valve seat 56 is of large enough diameter, and the spring 54 is so constructed as to pass large uid lows at a substantially constant, predetermined and relatively small pressure drop, so as not to materially effect the speed of operation of the servomotor. The closure member S2 is held olf its seat 56, at large uid iiow rates through means G and is moved toward the seat by spring 54 as the ilow diminishes. The chatter eliminating means G is further provided with a small opening 58 through the valve closure member 52 to permit pressure to equalize across the valve closure member 52 after it engages its seat.

ln the normal de-energized condition of the servomotor, a poppet member 34 is biased against flange 30 to hold the atmospheric valve closure member 26 ot of its seat 32, thereby permitting atmospheric pressure to be communicated to the internal power chamber 14 through foraminous spacer member 22 and a ring of lter material 60.. Actuating movement for the poppet member 34 will preferably be accomplished by means of a leverage system similar to that shown and described in the above referred to Hupp application. Actuation of the servo-motor is accomplished =by the relaxing of pressure against the end of the push rod 36, whereupon poppet member 34 moves to a position generally corresponding to that shown in the drawing. initial valve movement of the poppet member 34 permits the flange 30 to abut the atmospheric valve seat 32 to isolate atmospheric pressure from the power chamber 14, and subsequent movement opens communication between the power chamber 14 and the vacuum connection 5t). Assuming that a fast application has been called for by the operator and that poppet member 34 has been moved out of engagement with the ange 30, the pressure in the left-hand valve chamber 48 will be quickly raised to a level sucient to move the poppet member 52 out of engagement with the valve seat S6. A relatively small portion of the air ilow will of course be continually throttled through the opening 58 of the valve closure member 52, and the `bulk of the ow will pass through the annular space between the valve closure member 52 and the bore 62 as maintained by the guides 64. A throttling effect will of course be maintained between the closure member 52 and the valve seat 56 and this throttling effect will be substantially constant regardless of the quantity flowing once the closure member has been lifted from the valve seat 56.

When actuating movement of the poppet member 34 is stopped and the poppet member 34 becomes stationary, continued movement of the piston B causes the ange 30 of the atmospheric valve closure member 26 to approach the poppet member 34, thereby gradually reducing the flow of air out of the power chamber 14. It will be seen that very little friction or retarding force is exerted upon the piston B by reason of the diaphragm l2. By reason of the fact that mass set in motion tends to remain in motion, the valve seat 32 may be carried past the poppet member 34 by the piston B a sufficient distance to admit a small amount of atmosphere to the power chamber 14. This will, of course, cause the piston to move back and forth and the valve to chatter. Another condition tending to produce valve chatter may well be the fact that inertia lag of the piston B inherently permits too much vacuum to be communicated with the power chamber 14 for any particular set point of the poppet member 34, and the atmospheric valve member 26` must again be lifted oif its seat to bleed a slight amount of air pressure to the power chamber 14 to achieve 4 the balanced condition called for by the operator. Still other reasons may exist for explaining valve chatter in devices of the above described type.

While the chatter eliminating means G will be eifective in preventing chatter in control valves generally, it is particularly effective when used in conjunction with balanced valves of the above described type. It will be seen that the chatter eliminating means G produces a throttling effect which supplements that produced by the control valve E, as the control valve approaches its set point, thereby causing the piston B to slow down as the set point is reached. A further etect is produced in the device shown in the drawing, inasmuch as the back pressure produced in the valve chamber 48 by the chatter eliminating means G during flow is exerted upon the balancing diaphragm 40 in such direction as to cause the control valve E to approach a lapped condition at a modied set point which will be reached prior to the set point being called for by the operator. As the piston B moves into a position approaching the modified set point, flow through the control valve E is gradually diminished, reducing the amount of air flow being passed by the chatter eliminating valve means G. During the period of time that the control valve E is approaching its seat, valve closure member 52 approaches the valve seat S6 and thereafter dissipates the ditferential pressure across the valve closure member 52 through the throttle open ing 58. During the dissipation of the unbalanced pressure across the valve closure member 52, an increase in the differential pressure across the diaphragm 40 is experienced, which increase in dierential pressure is transmitted to the poppet member 34 of the control valve to urge it in a more open position. Chatter eliminating means G, therefore, will be seen to cause the control valve E to approach a modified set point which will always be approached prior to the set point being called for by the operator. By proper design of the chatter eliminating means G, the modified set point produced by the means G may be made to precede any set points that may be called for by an operator by an amount which will be greater than the amount of over shooting which can be experienced in the device by reason of its dynamic forces. While the above explanation represents one theory explaining the operation of the device, theories as to instability of servo-motor valving are in general quite complicated, and applicant does not wish to be limited to any particular theory of operation.

While the present invention has been described in considerable detail, application does not wish to be limited to the particular construction shown and described, as it will be apparent that other modifications and embodiments exist. One such modification would be to position the chatter eliminating means G in the passageway 46 on the opposite side of the control valve E. Were such modiiication to be made, however, it will be seen that the chatter eliminating means G would have to be positioned in the passageway 46 in such manner that large flows would be permitted from the power chamber 14 to the valve means E-in which case air flow into the power chamber 14 during retraction of the brakes would have to pass through the opening 58. This would make retraction of the brakes too slow for all practical purposes, and another passageway having a check valve therein would have to be used between the control valve E and the power chamber 14 to speed up the release of the unit. The valve shown in Figure 3 generally comprises an annular disc 70 having three inwardly turned ears 72 which slidably engage the sidewalls of the counterbore 74 that is provided in the outer end of the passageway 46. The center portion of the outer face, of the disc 70 is coated with an annular coating of rubber 76 the outer edges of which are normally biased against the annular retainer member 78 by a coil spring S0 to close olf the passageway. The radially inner edge of the rubber coating 76 forms a valve seat for the disc shaped closure member 82 having a stem4 84 which projects through a central `opening in the disc 70. The vinner end of the stem 70 is provided with a spring retainer 86, and the valve closure member 82 is biased into engagement with its seat by a coil spring 88 positioned between the retainer and the bottom side of the disc 70. v

It will be understood that should the valve structure shown in Figure 3 be used, the valve structure G shown in Figure 1 would not be used in the vacuum supply side 2 of the servo-motors control valve to the control valve E. Actuation of this embodiment as in the previously described embodiment is initiated by movement of the push rod 36 to the right, as seen in Figure l, permitting the poppet member 34 to be lifted from the flange 30 and thereby communicate vacuum to the passageway 46. Air pressure in the chamber 14 of the servomotor then causes the disc 70 to move inwardly away from the retainer member 78 and thereby permit air to liow through the clearance provided between the outer edge of the annular disc 70 and the sidewalls of the counterbore 74 as provided by the inwardly turned ear 72. As the set point for the valve structure E is approached, and the velocity of air flow through the passageway 46 diminishes, coil spring 80 will bias the annular disc 70 against the retainer member 78; and there- `after, pressure differential will be equalized across the .annular disc 70 through a small opening 90 in the valve closure member 82 which opening corresponds in size lto the opening 58 of the previous embodiment.

As in the previous embodiment deactivation of the servo-motor is accomplished by air flow through the passageway 46 back into the chamber 14. Air liow in vthis direction passes through the central opening in the annular disc 70 causing the valve closure member 82 to be biased oli of the radially inner end edge of the annular piece of rubber 76 to provide su-bstantially unrestricted flow for this return passage of-air. Still other modifications will occur to those skilled in the art, and it is my intention to cover hereby all adaptations, modifications, and uses thereof which come within the practice of those skilled in the art to which the invention relates.

I claim:

l.. A iiuid pressure servo-motor control system comprising: a servo-motor housing; a movable wall in said housing forming an enclosed chamber with said housing, said movable wall having little frictional resistance to motion; a fluid pressure source which when communicated to said chamber produces movement of asid movable wall; a throttling control valve for regulating lluid flow in a first direction between said source and said chamber, said valve including rst and second relatively movable portions one of which is manually actuatable and the other of which is moved by said movable wall to provide follow-up of said manually actuatable portion by said movable wall; an anti-chatter valve in series llow relationship with respect to said control valve, said antichatter valve having a valve closure member which opposes ow therethrough in said irst direction with generally predetermined force and being movable by the force of liuid owing therethrough from a rst upstream position where it has but a small liow capacity to a downstream position where it is capable of passing the full ow capacity of said control valve at a generally predetermined pressure diierential; the amount of resistance to ow when said valve closure member is in its first position, and the amount of biasing of said valve closure member being sized with respect to the frictional resistance of said movable wall, its inertia, and the flow capacity of said control valve as to prevent said movable wall from appreciably overshooting the position called for by said manually actuated portion of said control valve regardless of the speed at which it is moved.

2. A liuid pressure servo-motor control system comprising: a servo-motor housing; a' movable vwall in said housing forming an enclosed chamber with said housing, said movable wall having little frictional resistance -to motion; a fluid pressure source which when communicated to said chamber produces movement of said mova able wall in a first direction; a throttling control valve carried by said movable wall for regulating lluid flow between said source and said chamber, said valve including a manually actuated valve closure member which when moved in said rst direction opens communication between said source and said chamber to provide followup of said manually actuable closure member by said movable wall; an anti-chatter valve in series ow relationship with respect to said control valve, said antichatter valve having a valve closure member which opposes said actuating uid flow with generally predetermined force and being movable by the force of liuid flowing therethrough from a lirst upstream position where it has but a small ow capacity to a downstream position where it is capable of passing the full flow capacity of said control valve at a generally predetermined pressure differential; the amount of resistance to flow ;in said rst position, and the amount of biasingof said valve closure member being so sized with respect to the frictional resistance of said movable wall, its inertia, and the llow capacity of said control valve as to prevent said movable wall from appreciably overshooting theposition called for by said manually actuated valve closure member regardless of the speed at which it is moved.

3. A Huid pressure servo-motor control system comprising: a servo-motor housing; a movable Wall in said housing forming an enclosed chamber with said housing, said movable wall having little frictional resistance to motion; a lluid pressure source which when'communicated to chaid chamber produces movement of said movable wall in a first direction; a throttlingvcontrol valve car. red by said movable wall for regulating fluidow between said source and said chamber, said valve including a manually actuatable valve closure member which when moved in said first direction opens communication between said source and said chamber to provide followup of said manually actuatable closure member by said movable wall; an anti-chatter valve in series tlow relationship with respect to said control valve, said antichatter valve comprising a lirst flow path having a valve seat facing in the downstream direction of saidl actuating tluid ow and having a valve closure member biased against said valve seat with vgenerally predetermined force, said flow path having passages of relatively large capacity to conduct flow away from said valve seat with little flow resistance when said valve 'closure member is oit of its seat; and a second flow path in parallel owfrelationship with respect to said first flow path, said second llow path having an appreciably smaller flow capacity than said lirst flow path; the amount of resistance to ow of said second flow path, and the amount of biasing of said valve closure member being so sized Withrespect to the frictional resistance of said movable Wall, its inertia, and the liow capacity of said control valve as to prevent said Imovable wall from appreciably overshooting the position called for by said manually actuated valve closure member regardless of the speed at which it is moved.

4. A uid pressure servo-motor control system comprising: a servo-motor housing; a movable Wall in said housing forming an enclosed chamber with said housing, said movable wall having little frictional resistance to motion; a fluid pressure source which when communicated to said chamber produces movement of said movable wall; a throttling control valve for regulating iluid ow in 4a rst direction between said source and said chamber, said valve including rst and second relatively movable portions one of which is manually actuatable and the other of which is moved by said movable wall to provide follow-up of said manually actuatable portion by said movable wall; an anti-chatter valve in series ow relationship with respect to said control valve, said anti-chatter valve comprising a first flow path having a valve seat facing in the downstream direction of said actuating fluid ilow and having a valve closure member biased against said valve seat with generally predetermined force, said anti-chatter valve having passages of relatively large capacity to conduct flow away from said valve seat With little flow resistance when said valve closure member is oil of its seat; and a second flow path in parallel ow relationship with respect to said rst ow path, said second How path having an appreciably smaller ow capacity than said rst ow path; the amount of resistance to flow of said second flow path, and the amount of biasing of said Valve closure member being so sized with respect to the frictional resistance of said movable wall, its inertia, and the flow capacity of said control valve as to prevent said movable wall from appreciably overshooting the position called for by said manually actuated portion of said control valve regardless of the speed at which it is moved.

5. A uid pressure servo-motor control system comprising: a servo-motor housing; a movable wall in said housing forming an enclosed chamber with said housing, said movable wall having little frictional resistance to motion; a fluid pressure source which when communicated to said chamber produces movement of said movable wall; a throttling control valve for regulating uid ilow in a first direction between said source and said chamber, said valve including rst and second relatively movable portions one of which is manually actuatable and the other of which is moved by said movable wall to provide follow-up of said manually actuatable portion by said movable wall; an anti-chatter valve in series ow relationship with respect to said control valve, said antichatter valve comprising a valve seat facing in the down stream direction of said actuating tluid ow and having a valve closure member for abutment with said valve seat; a spring biasing said closure member against said seat with predetermined force; said anti-chatter valve having passages of relatively large capacity to conduct ow away from said valve seat with little flow resistance when said valve closure member is off of its seat; and an orifice through said valve closure member, said orifice having an appreciably smaller ow capacity than that provided between said closure member and said valve seat; the resistance to flow of said orifice, and the strength of said spring being so sized with respect to the frictional resistance of said movable wall, its inertia, and the ow capacity of said control valve as to prevent said movable wall from appreciably overshooting the position called for by said manually actuated portion of said control valve regardless of the speed at which it is moved.

6. A iluid pressure servo-motor control system comprising: a servo-motor housing; a movable wall in said housing forming an enclosed chamber with said housing, said movable wall having little frictional resistance to motion; a vacuum source which when communicated to said chamber produces movement of said movable wall in a rst direction; a throttling control valve carried by said movable wall for regulating fluid ow out of said chamber, said valve including a manually actuated valve closure member which when moved in said rst direction opens communication between said source and said chamber to provide follow-up of said manually actuatable valve closure member by said movable wall; an anti-chatter valve downstream of said control valve, said anti-chatter valve comprising a valve seat facing in the direction of fluid ow out of said chamber and having a valve closure member for abutment with said valve seat; a spring biasing said closure member against said seat with predeter` mined force, said anti-chatter valve having passages of relatively large capacity to conduct flow away from said valve seat with little flow resistance when said valve closure member is orf of its seat; and an orifice through said valve closure member, said orice having an appreciably smaller flow capacity than that provided between said closure member and said valve seat; the amount of resistance to ow of said orifice, and the strength of said spring being so sized with respect to the frictional resistance of said movable wall, its inertia, and the flow capacity of said control valve as to prevent said movable wall from appreciably overshooting the position called for by said manually actuated valve closure member regardless of the speed at which it is moved.

7. In a uid flow control circuit, a high pressure charnber, an intermediate pressure chamber, a poppet valve for controlling ilow through said circuit, a movable wall in said intermediate chamber operatively connected to said poppet valve for opposing pressure forces across said poppet valve, a back pressure valve in said circuit for controlling the pressure in said intermediate pressure chamber in such manner as to cause said movable wall to urge said poppet valve toward a closed condition when flow is experienced through said circuit, and restricted flow communicating means across said back pressure valve for permitting the differential across said back pressure valve to be dissipated as flow through said circuit approaches zero.

8. In a fluid ow control circuit for a iluid pressure servo-motor and the like, a valve body having a valve chamber therein, movable walls in opposite ends of said valve chamber, said movable walls being subjected to atmospheric pressure on their outer surfaces, a valve seat intermediate the ends of said valve chamber, a poppet valve in said valve chamber constructed and arranged to abut said seat and separate said valve chamber into opposing end chambers, first means communicating one of said opposing end chambers to a high pressure source, second means communicating the other of said opposing end chambers to a low pressure source, means operatively connecting said movable walls to said poppet valve in such manner to substantially balance the forces on said poppet valve, a back pressure valve in one of said iirst and second means opposing flow through said circuit, and restricted flow communicating means across said back pressure valve for permitting the differential pressure across said back pressure valve to be dissipated as flow through said circuit approaches zero.

References Cited in the file of this patent UNTED STATES PATENTS 1,105,061 Carpenter July 28, 1914 1,801,483 Bragg et al Apr. 2l, 1931 2,039,095 Lower Apr. 28, 1936 2,291,881 Coffey Aug. 4, 1942 2,366,382 Burton lan. 2, 1945 2,458,803 Stelzer Jan. 1l, 1949 2,722,199 Blanchette Nov. l, 1955