WO1984003371A1 - Electrically-controlled rotary actuator - Google Patents
Electrically-controlled rotary actuator Download PDFInfo
- Publication number
- WO1984003371A1 WO1984003371A1 PCT/US1984/000233 US8400233W WO8403371A1 WO 1984003371 A1 WO1984003371 A1 WO 1984003371A1 US 8400233 W US8400233 W US 8400233W WO 8403371 A1 WO8403371 A1 WO 8403371A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- circuit board
- terminating
- set forth
- invention set
- actuator
- Prior art date
Links
Classifications
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D3/00—Control of position or direction
- G05D3/12—Control of position or direction using feedback
- G05D3/14—Control of position or direction using feedback using an analogue comparing device
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
- F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
- F16K31/043—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
Definitions
- This invention relates generally to actuators for positioning control of devices coupled thereto and more particularly to electrically controlled actuators for positioning of valves, mechanical dampers and the like as employed in process control systems.
- the invention is particularly suited for use in systems related to heating, ventilating and air conditioning applications.
- Process control systems frequently employ valves which may be positionably adjusted for controlling the flow of fluids within a conductor system such as a pipeline.
- Other types of fluid flow controlling devices often encountered in process control systems include dampers which may be actuated for controllably modulating the flow of gases therethrough.
- HVAC heating, ventilating and air conditioning
- HVAC systems which usually employ a plurality of air handling units comprising interconnected ductwork having mechanical dampers associated therewith.
- the ductwork and dampers cooperate for controlling the flow of outside ambient air into a conditioned space, for controlling the flow of air from the space to the ambient and for controlling air flow between cool and warm air ducts.
- HVAC systems also employ actuator-positioned valves whereby the flow of chilled or heated water through
- OMPI heat exchanger coils may be controlled in accordance with the air temperature which is desired to be maintained as the air passes over such coils for air temperature- regulating purposes.
- Liquid flow control valves and fluid controlling dampers of the aforementioned type are available in a wide variety of sizes and torque requirements, such sizes being generally related to the size of the air handling unit with which they may be associated. While it is known to utilize electrically-driven rotary actuators for positioning such valves and dampers, the wide range of torque requirements of such devices has heretofore necessitated that such actuators be configured in a variety of drive motor torque output ranges, enclosure sizes and gearing arrangements.
- An electrically-controlled rotary actuator which takes maximum advantage of parts commonality and is adapted to be configured for providing any one of several rated output torques, which includes a power transmission having drive elements capable of being formed of several disparate materials selected in view of such torque requirements and which is adapted to receive a variety of electric controls arranged in plug-in modular form for simplified manufacture, inventory and field installation would be a significant advance over the prior art.
- the motor-driven rotary actuator of the present invention includes an electric drive motor adapted to be configured for providing one of a plurality of output torques.
- a power transmission including a rotatable output shaft is coupled to the drive motor and includes drive elements adapted to be formed of disparate materials selected for transmitting a particular output torque.
- An electric controller is coupled to the drive motor for providing rotation positioning control of the actuator output shaft in response to analog command signals.
- the controller is preferably embodied to include a plurality of circuit boards' selectable for providing a variety of control configurations and adapted to be electrically coupled one to the other by multiple conductor plug-in connectors.
- a preferred drive motor is of the single phase, permanent split capacitor type which may be adapted by suitable stator winding configuration and phase-shifting capacitor selection to provide any one of several rated output torques.
- a multiple-gear power transmission including an output shaft is coupled to the drive motor and includes a plurality of gear elements which may be formed of cut steel, powdered metal and/or a plastic material with the material of specific gear elements being selected in view of the desired actuator output torque.
- the gear elements and their related support shafts utilize the same shaft centerlines and mounting structure irrespective of the materials from which the elements may be formed.
- the electric controller includes a first control circuit having means for generating a signal representative of the actual angular position of the output shaft and static switching means for controllably de-energizing the drive motor.
- a second control circuit is electrically coupled to the first control circuit, is responsive to proportional voltage signals and includes signal shift circuit means for selectively converting a first input voltage signal occurring within a predetermined first range to a second input voltage within a predetermined second range in a manner such that a second voltage within the second range is representative of a first voltage within the first range.
- a separately mounted first terminating means may be provided for simplified attachment of field wiring brought into the actuator enclosure.
- the second control circuit and the first terminating means may be replaced by other control circuits adapted for providing other, specific control modes.
- Spring return and retarder brake assemblies may optionally be incorporated as dictated by the requirements of the specific application.
- the spring return assembly may be coupled to the exterior of a common housing adapted to accommodate the drive motor, power transmission and electric controller of the embodiments.
- Yet another object of the present invention is to provide a rotary actuator having a power transmission which includes drive elements adapted to be formed of disparate materials selected for the transmission of one of several output torques.
- Still another object of the present invention is to provide a rotary actuator which includes an electric controller for providing rotation positioning control of the actuator output shaft.
- Still another object of the present invention is to provide a rotary actuator which may be adapted to one of a variety of control configurations by using plug-in circuit boards.
- Another object of the present invention is to provide a rotary actuator which may be readily adapted to incorporate spring return and retarder brake features.
- FIGURE 1 is a front elevation view of the actuator of the present invention
- FIGURE 2 is a side elevation view of the actuator of FIGURE 1 taken substantially along the plane 2-2 thereof with portions shown in cross-section and other portions shown in full representation;
- FIGURE 3 is a front view of a first embodiment of the actuator drive motor taken along the plane 3-3 of FIGURE 2;
- FIGURE 4 is a side elevation view of the motor of FIGURE 3 taken along plane 4-4 thereof and with portions shown in cross-section and other portions shown in full representation;
- FIGURE 5 is a side elevation view of a second embodiment of the motor and generally corresponding to the plane of view of FIGURE 4;
- FIGURE 6 is a side elevation view of the actuator power transmission means
- FIGURE 7 is an end elevation view of the power transmission means taken along the plane 7-7 of FIGURE 6 and further depicting a brake spring;
- FIGURE 8 is a mechanical schematic view of the drive elements of the power transmission means and further including the motor pinion gear;
- FIGURE 9 is a tabulation depicting preferred materials from which the drive elements of FIGURE 8 may be formed;
- FIGURE 10 is a side elevation view generally of the actuator of FIGURE 1 taken along the plane 2-2 thereof and further generally depicting the optional spring return mechanism and the location of additional circuit boards used in certain embodiments, with portions shown in cross section, other portions broken away and yet other portions shown in phantom;
- FIGURE 11 is a view of the spring return mechanism taken along the plane 11-11 of FIGURE 10 with portions shown in cross-section, other portions broken away and yet other portions shown in phantom.
- FIGURE 12 is a cross-sectional view of the spring return mechanism taken along the line 12-12 of FIGURE 11;
- FIGURE 13 is an end elevation view of a second embodiment of a gear assembly of the power transmission means taken along the plane 13-13 of FIGURE 6;
- FIGURE 14 is a bottom plan view of a portion of the gear assembly of FIGURE 13 taken generally along the line 14-14 thereof and with portions shown in cross-section and other portions shown in full representation;
- FIGURE 15 is a side elevation view of a third embodiment of the actuator drive motor and generally corresponding to the plane of view of FIGURE 4, with portions shown, in cross section and other portions shown in full representation;
- FIGURE 16 is a side elevation view of a fourth embodiment of the actuator drive motor and generally corresponding to the plane of view of FIGURE 4, with portions shown in cross section and other portions shown in full representation;
- FIGURE 17 is an electrical schematic diagram of the first circuit of the actuator electric control means with a portion shown in phantom;
- FIGURE 18 is an elevation view of the first circuit board of the control means and embodying the circuit of FIGURE 17;
- FIGURE 19 is an electrical schematic diagram of the second circuit of the actuator electric control means
- FIGURE 20 is a front elevation view of the actuator contactor disk;.
- FIGURE 21 is a side elevation view of the contactor disk taken along the plane 21-21 of FIGURE 20;
- FIGURE 22 is an electrical schematic diagram of the first terminating means of the electric control means, the same formimg a part of the first embodiment of the actuator;
- FIGURE 23 is a plan view of the first terminating means circuit board and embodying the circuit of FIGURE 22;
- FIGURE 24 is an elevation view of second circuit board of the control means and embodying the circuit of FIGURE 19;
- FIGURE 25 is an electrical schematic diagram of the third circuit of the control means, the same forming a part of the second embodiment of the actuator, and;
- FIGURE 26 is an electrical schematic diagram of the second terminating means of the control means, the same forming a part of the second embodiment of the actuator.
- the actuator 10 is shown to include a partitioned enclosure 11 having a first compartment 13 for receiving the electric drive motor 15 and power transmission 17 and a second compartment 19 for receiving the electric controller 21 and termination board 23 components.
- the enclosure 11 includes a housing 25 having a base member 27, a pair of vertically disposed generally parallel side members 29 arranged in spaced relationship one to the other and a partition 31 for supporting the output shaft 33 and for defining a barrier between the first compartment 13 and the second compartment 19. While the base member 27, the side members 29 and the partition 31 may be formed as separate pieces for assembly, it is preferred that the housing 25 be formed as an integral unit as, for example, by die casting.
- the power transmission 17 includes a generally planar face member 35 adapted to abut the base member 27, the side members 29 and the partition 31 to define the first compartment 13.
- An oil seal 37 is disposed between the face member 35 and the base member 27, side members 29 and partition 31 for the retention of lubricating oil which may be introduced into the first compartment 13 through a fill hole sealable by a plug 39.
- a generally planar end panel 41 and top panel 43 cooperate with the partition 31, the face member 35 and the side members 29 for defining the second compartment 19 used for receiving the electric controller 21 components.
- An optional control transformer (not shown) may be incorporated upon the top panel 43 to accommodate line voltages other than those for which the motor 15 is constructed.
- a termination board 23 is received atop the partition 31 for the connection of field wiring brought into the enclosure 11 through apertures 45 within a side member 29 and such connection may be directly to the terminals 47 or through the control transformer.
- FIGURES 2, 3 and 4 A first embodiment of the electric drive motor 15, useful in actuators incorporating a spring return feature, is shown in FIGURES 2, 3 and 4 to include a laminated stator 49 having multiple poles 51, a rotor assembly 53 and a pair of end brackets 54 for supporting the stator 49 and rotor assembly 53 in an operative relationship.
- the rotor assembly 53 includes a rotor 55 disposed upon a shaft 57 supported for rotation by a pair of generally spherical, self-aligning bearings 59, preferably of bronze.
- the shaft 57 has a first pinion gear 63 affixed thereto for drivingly coupling the motor 15 with the power transmission means 17.
- the pinion gear 63 has a face disc 65 attached thereto at its first end 61, the disc 65 being utilized for braking as described in greater detail below.
- a bearing strap 67 is disposed adjacent the second end of the shaft 57 and is retained in contact with the shaft end by ' a clip 69 configured to engage elongate apertures 71 in the adjacent bracket 54.
- the bearing strap 67 may be formed of any suitable bearing material, as, for example, of nylon. In order to provide an acceptably long operating life of the bearing strap 67 and of the brake spring, described in detail below, it is preferred that both ends of the motor shaft 57 be hemispherically shaped and highly polished.
- the motor 15 is supported within the first compartment 13 upon spacers 73 or standoff studs (not shown) and is affixed to the power transmission second support plate 75 with suitable fasteners as, for example, by screws.
- the motor leads 77 may be brought out through the partition 31 using insulated feedthrough studs 79.
- OMPI__ actuator 10 from which the spring return feature is omitted and which is intended to retain the actuator output shaft 33 at an angular position upon motor de-energization.
- a retarder brake 81 be arranged therewithin for retaining the actuator output shaft 33 at its last-commanded angular position during quiescent conditions when the motor 15 is de-energized.
- the motor 15 incorporates a pair of opposingly arranged braking surfaces 83, one each disposed upon the inward surface of the face disc 65 and upon a portion of the outward surface of the adjacent bracket 54.
- the motor shaft 57 is permitted to move longitudinally in a first, brake-engaging direction under the urging of a leaf type brake spring 85 and during those periods when the motor 15 is de-energized. Movement of the shaft 57 and rotor 55 in this manner will result in a slight displacement of the rotor 55 to a position somewhat laterally off center with respect to the stator 49 and its magnetic field. Upon motor energization, the rotor 55 will seek the center position of maximum field strength, resulting in slight movement of the rotor 55 and shaft 57 to overcome the urging of the brake spring 85 and disengage the braking surfaces 83.
- the drive motor 15 be of the single phase, permanent split capacitor type whereby any one of a plurality of output torques may be achieved by appropriate selection of the stator winding wire size and number of turns and by the selection of the appropriate phase shifting capacitor.
- the windings are electrically insulated from the poles by a dielectric material disposed therebetween such as by plastic sleeves
- the drive motor 15 with spring return constructions omitted may have a first configuration for providing a preferred rated output shaft torque of 35 pound-inches within a preferred torque range of 25-55 pound-inches; a second configuration for providing a preferred rated output shaft torque of 75 pound-inches within a preferred torque range of 55-110 pound-inches and a third configuration for providing a preferred rated output shaft torque of 150 pound-inches within a preferred torque range of 110-160 pound inches.
- An 8-pole motor 15 is preferred for operation at 60 Hz, the motor 15 being internally connected to define two phases of four poles each.
- the power transmission means 17 is shown to include a face member 35 having a rotatable output shaft 33 protruding therethrough and a gear assembly 87 supported thereon for transmitting driving torque from the electric motor 15 to a valve, damper or other device coupled to the shaft 33 for positioning control.
- the ' power transmission 17 includes a first bull gear 89 for driven engagement with the motor pinion gear 63, intermediate gear means 91 and an output bull gear 93 affixed to and concentric with the longitudinal centerline of the output shaft 33.
- the first bull gear 89 and its related, concentrically arranged first pinion gear 95 are affixed to a first spindle 97, the latter being rotatably supported by bronze bushings 99 disposed in apertures in the first plate 101 and second plate 75.
- the face member includes an enlarged shaft boss 103 having a first pocket 105 formed therein and sized .to receive a suitable first bearing 107 with pressed fit.
- a second, enlarged pocket 109 is formed in the outer face of the boss 103 concentric with the first pocket 105 and the output shaft 33 and is sized to receive a lip-type oil seal 111 for the retention of lubricating fluid within the first compartment 13.
- the partition 31 includes a third pocket 115 formed therein and sized to receive a second bearing 117 with pressed fit, the first bearing 107 and the second bearing 117 thereby cooperating to rotatably support the output shaft 33.
- the shaft and motor bearings 59, 107, 117 may be of any suitable construction as, for example, sintered bronze, nylon or DELRIN, a trademarked product of E. I. Du Pont, preferably filled with a dry lubricant.
- a sealing disk 119 and retaining washer 121 are disposed outwardly of the second bearing 117 in a suitable pocket formed in the partition 31 for providing lubricating oil retention.
- Those drive elements comprising the intermediate gear means 91 are arranged for rotatable, driving engagement one with the other and are rotatably disposed upon suitable hardened steel spindles 123 which are rigidly, nonrotatably supported between the first plate 101 and the second plate 75.
- the plates 75, 101 are maintained in a parallel, spaced-apart relationship by standoff tubes 125 with the gear assembly 87 being attached to the face member 35 by suitable fasteners 127 such as cap screws or bolts which extend through the standoff tubes 125 and are received within internally threaded bosses 129 formed in the face member 35.
- the output bull gear 93 and its associated first bearing 107 and output shaft 33 are restrained from significant longitudinal movement by an inwardly projecting shoulder 131 of the first bearing 107 on the one hand and by a restraining fork 133 on the other hand. Due to manufacturing tolerances, it may be desirable to place one or more shims 135 between the fork 133 and the bushing 113 in a known manner to provide a specified maximum end play.
- the fork 133 is formed in the second plate 75 and has an upwardly projecting dimension selected to overlap the face end of the shaft bushing 113 or a shim 135, as the case may be.
- the length of the shaft bushing 113 is preferably selected to be only slightly less than the distance between the inward shoulder 131 of the first bearing 107 and the opposing, inward face of the restraining fork 133.
- the output bull gear 93 will be maintained in full driven engagement with the intermediate gear means 91 while yet providing sufficient space between the bearing 107 and the bushing 113 and between the bushing 113 and the fork 133 so as to permit free shaft rotation and also to permit lubricating fluid to flow therebetween.
- the power transmission means 17 of the preferred embodiment comprises ten driving elements, including the motor pinion gear 63 and the output bull gear 93, arranged to provide five gear reductions resulting in an overall ratio of about 3200 revolutions of the motor shaft 57 for each revolution of the output shaft 33.
- a unique feature of the power transmission means 17 is that its drive elements are adapted to be formed of disparate materials which result in lowered manufactured cost and acceptable field life consistent with the wide variety of torques required to be transmitted thereby. Further, the spindles 97, 123 including the output shaft 33 used to support the drive elements are disposed upon rotational axes, the locations of which remain fixed irrespective of the material from which the drive elements are formed.
- FIGURE 9 comprises a table depicting the materials used to form the various drive elements for each of the three output torque ranges of the preferred embodiments.
- Pinion gears 63, 95, 137, 139 and 141 and bull gears 89, 142, 143, 145 and 93 of FIGURE 8 correspond to those same elements in FIGURE 9.
- appropriate materials may include a DELRIN 500 acetal compound or of 6/6 nylon, glass and TEFLON filled as available from LNP Corporation under catalog number RFL4036.
- DELRIN and TEFLON are trademarks of E. I. Du Pont. Error tolerance for composite error and functional tooth thickness of all drive elements is to be determined by the composite method of gear inspection as described in Appendix A of the AGMA Gear Handbook, Volume 1, AGMA 390.03 of 1972. AGMA class 1 master gear with type 2 calibration is preferred. Referring next to FIGURES 2, 10, 11 and 12, it may be desirable in certain applications to cause the actuator output shaft 33 to be returned by spring force to a predetermined reference position whenever the drive motor 15 is de-energized.
- an elongated output shaft 33' may be substituted for that of standard length to permit the mounting of a spring return assembly 147 upon the auxiliary shaft end 149 opposite the output end.
- a preferred spring return assembly 147 is shown in FIGURES 11 and 12 to include a housing member 151 for confining a spring 153 having a first tang end 155 thereof in torque transmitting engagement with a hub 157 formed on the output shaft 33' adjacent the auxiliary end 149.
- a second tang end 159 engages a notch 161 formed in the housing member 151 for spring retention.
- a preferred spring return assembly 147 includes a spirally wound spring 153 formed of a flat ribbon, preferably metallic. Referring particularly to FIGURE 12, in order to assure positive spring return of the output shaft 33' to a reference position, it is preferred that the spring 153 be preloaded prior to attachment of the spring return assembly 147 upon the actuator 10.
- the hub 157 includes a plurality of cylindrically shaped stop stud pockets 163 formed to a depth in the first face 165 of the hub 157 in a circu ferentially spaced apart relationship one to the other and having their longitudinal axes parallel to the rotational axis of the hub 157 and the output shaft 33'.
- a plurality of counterbores 167 are formed in the hub second face 169 to have their longitudinal centerlines coincident with the corresponding centerline of the related stop stud pocket 163.
- a longitudinal passage 171 is concentrically formed between each counterbore 167 and its related pocket 163 and is sized to receive a stud retaining screw 173 with slight clearance.
- the hub 157 When it is desired to preload the spring return assembly 147, the hub 157 is manually rotated in a spring preloading direction until a desired preload is obtained.
- An appropriate stop stud 175 is thereupon inserted within a stud pocket 163 in a manner to prevent spring unwinding and thereby retain the preload.
- An appropriate stud 175 will have a threaded hole in the bottom thereof for receiving the retaining screw 173 and will have a length selected such that when the stud 175 is bottomed in its pocket 163, its projecting shoulder is of a height sufficient to engage a tang 177 formed in the backplate of the housing member 151.
- Mounting feet 179 having elongate apertures 181 formed therein are provided for fastening the spring return assembly 147 to the actuator enclosure 11.
- the spring 153 may be configured from ribbons of varying thicknesses, widths, lengths or a combination thereof to provide varying positioning torques.
- the spring preload would be selected such that when the spring return assembly 147 is combined to an actuator 10 having a motor 15 of the second configuration, the preferred available output shaft torque is 25 Ib-in.
- a second preferred spring return configuration would employ a preload to result in an output shaft torque of 50 Ib-in. when combined with a motor 15 of the third configuration.
- FIGURES 13 and 14 depict a second embodiment of the gear assembly 87 while FIGURE 15 depicts a third embodiment of the motor 15. While the view of FIGURE 14 is taken generally along the line 14-14 of FIGURE 13, it should be understood that aspects of the adjustment bracket 183 described below are also included for clarity.
- the first bull gear 89 and first pinion gear 95 are shown in FIGURE 14 to be rotatably supported upon a non-rotating axle 185, preferably formed of hardened steel.
- the shoulder 187 of the first bull gear 89 extends through an opening 189 in the second plate 75 with slight clearance therebetween to permit adjustment as described below.
- the bull gear 89 and pinion gear 95 may be fabricated as a unitary structure. If disparate materials are required for the application, the pinion gear 95 will preferably include a neck member 191 sized to be received in a cavity within the first bull gear 89 with press fit. In the alternative, the mating portions of those gears 89, 95 may be formed to closely fitted, torque transmitting shapes such as a square or hexagon.
- a first end 193 of the axle 185 is press fitted to the first plate 101 while a second end 195 is supported by an aperture in an adjustment bracket 183, the latter having a first, pivot point 197 and a second, clamping end 199.
- An end 200 of the rotor shaft 201 is secured by press fit within a hole in the second plate 75 in a manner such that the motor pinion gear 203 is in driving engagement with the first bull gear 89.
- the pivot point 197, the center line of the axle 185 and the rotor shaft 201 center line define approximately a right angle.
- a stud and clamping screw 205 are disposed at the clamping end 199 of the bracket 183 and positioned to engage a slot 207 formed at the bracket end 199.
- the rotor assembly 209 includes a pinion gear portion 203, a rotor 211 and a brake member 213 assembled as a unitary structure and rotatably supported upon a stationary shaft 201, preferably formed of hardened steel.
- a generally C-shaped magnet clip 215 is received through slots 216 formed in the bracket 54 and has an electromagnetic coil 217 wound thereabout for brake actuation. If motor braking is desired, the coil 217 is actuated whereupon the rotor assembly 209 including the brake member 213 is magnetically drawn to the magnet clip 215 for frictional engagement therewith. Upon de-energization of the coil 217, a spirally wound biasing spring 219 urges the rotor assembly 209 to a position whereby the brake member 213 and the magnet clip 215 are in a spaced-apart relationship.
- a feature of this embodiment is that energization of the coil 217 and therefore actuator braking may be selectively controlled by external means.
- the motor stator 49 and bracket 54 are supported upon the second plate 75 by a pair of
- a gage block temporarily fitted at the position of the rotor assembly 209.
- a suitable gage block will have a diameter only slightly in excess of the diameter of the rotor 211.
- annular friction disk 221 is affixed to the motor brake member 213 for frictional engagement with a second, similar disk 223 affixed to the bracket 54.
- a coiled spring 225 is disposed upon the shaft 201 intermediate the first pinion gear 203 and the second plate 75 for biasing the rotor assembly 209 to a braking position whenever the motor is de-energized.
- the electric control means 21 of the embodiments provides for rotation positioning control of the output shaft 33 in response to analog command signals. Positioning is by comparing a command signal representative of the desired shaft position with a feedback signal representative of the actual position of the shaft and selectively generating an error signal based thereon.
- the electric control means 21 is shown to include a first control circuit 227 (FIGURE 17) having first means 229, preferably a potentiometer, for generating a signal representative of the actual angular position of the output shaft 33 and static switch means 231 for controllably energizing and de-energizing the drive motor 15.
- a trimming potentiometer 233 permits calibration to nullify the tolerances of the potentiometer 229 and the travel adjustment potentiometer 235 described in greater detail below.
- a phase-shifting capacitor 237 cooperates with the
- the electric control means 21 also includes a second control circuit 239 (FIGURE 19) coupled to the first circuit 227 and being responsive to proportional voltage command signals which may be received thereat from a separately mounted proportional controller
- the second control circuit 239 includes integrated circuit means 241 for controllably triggering the static switch means 231 to effect bidirectional rotation of the drive motor 15 between first and second angular positions of the output shaft 33 as dictated by the proportional voltage signals.
- the first control circuit includes an actuator position feedback potentiometer 229, a plurality of motor control static switches 231 such as static triacs and a capacitor 237 coupled in series with its current limiting resistor 245.
- the potentiometer 229 provides a voltage signal representative of the actual output shaft position while the switches 231 are responsive to triggering signals received from the second control circuit 239 for selectively energizing and de-energizing the drive motor 15 in the absence of a triggering signal to either switch 231. Selective triggering of one of the two switches 231 will result in clockwise or counterclockwise rotation of the output shaft 33.
- a biasing resistor 247 may be coupled in parallel with one of the switches 231 for partially energizing the motor 15 to counterbalance the torque generated by the spring return assembly 147.
- the potentiometer 229 is shown to include a pair of circular, generally concentric conductive plastic resistor ribbons 249 disposed upon a 0.005 inch APTON substrate which is attached to the circuit board 251 embodying the first control circuit 227 and an electrically conductive shorting clip 253 disposed upon a movable contactor disk 255, the latter being formed of an insulating material.
- the resistor ribbons 249 include an interrupted, generally circular outer resistance ring 257 and a concentric, inner resistance ring 259 with each of the rings 257, 259 having connecting posts 261 coupled to other components of the first control circuit 227 as shown in FIGURE 17.
- the shorting clip 253 is formed of a conductive spring material and includes a plurality of spaced apart fingers 263 for contacting the resistance rings 257, 259 and electrically shorting thereacross at the points of contact.
- the contactor disk 255 includes an aperture 265 sized to snugly engage the output shaft 33 for coincident rotation therewith and is held in resistance ring contacting engagement by a wiper clamp 267 attached to the shaft 33 with a setscrew.
- the disk 255 includes a truncated cone-shaped nipple 269 protruding therefrom to engage a drive aperture formed in the clamp 267.
- KAPTON is a trademark of E. I. Du Pont.
- the second control circuit 239 includes a halfwave rectified, unregulated power supply 271 for generating a DC voltage by the application of an AC voltage at terminals TI and T2 to a diode 273 and capacitor 275.
- a voltage regulator chip 277, a transistor 279 and a plurality of resistors 281 cooperate for providing +15VDC and +12VDC regulated supplies which are available at the pins VB and 10 respectively.
- the floating regulator 277 maintains a constant 1.25VDC across the resistor 281 designated R302 and with the second control circuit 239 constructed and arranged as shown in FIGURE 19, the voltage at the emitter of the transistor 279 is maintained at approximately 12VDC.
- the resistor 281 designated R307 provides a current limiting function for the +12VDC supply.
- the second control circuit 239 also includes an integrated circuit chip 241 for providing clipper, amplifier, comparator and output functions.
- a chip 241 which has been found useful in the second control circuit 239 is available from Johnson Controls, Inc. of Milwaukee, Wisconsin under part no. ICL18-1.
- the second control circuit 239 further includes a signal shift circuit 243 for selectively converting a first input voltage signal occurring within a predetermined first range to a second input voltage within a predetermined second range in a manner such that a second voltage within the second range is representative of a first voltage within the first range.
- the first range is +6 to +10VDC while the second range is 0 to -2VDC.
- Signal shifting is by biasing the emitter of a transistor 283 to a DC voltage established by the resistors 285.
- this voltage is 5.4VDC.
- the transistor 283 commences conduction when its base voltage rises to a level equivalent to the voltage established by the resistors 285 added to the base-to-emitter voltage or a value of approximately 6VDC.
- the control output voltage available at "8" terminal decreases from 0VDC, reaching a value of -2VDC when the second input voltage reaches a value of +10VDC, the voltages occurring within the first range and those resulting in the second range having a linear relationship one to the other.
- the second input voltage is coupled by a diode 287 into the "8" terminal.
- the value of a first input voltage signal may be greater or less than- the voltage value boundaries defining the first input range and such value may be, for example, 0 to +24VDC.
- construction and arrangement of the second control circuit 239 as shown and described will cause it to be unresponsive to all first input voltage signals other than those occurring within the first input range.
- the component values described herein are selected such that when the transistor 283 becomes saturated to permit the flow of base current, the maximum voltage on the resistor 285 designated R312 is limited to 9VDC maximum even though the value of the first input signal may exceed 9VDC.
- the shift circuit 243 further include a polarity protection means for isolating the shift circuit 243 from such voltages.
- a diode 289 is coupled at the base of the transistor 283.
- a protective circuit for damage prevention in the event of a power supply short circuit condition. Accordingly, a current demand imposed upon the +12VDC supply which exceeds the saturation current of the transistor 279 will cause the transistor 279 to exhibit a flow of base current which results in a decrease in voltage drop across the resistor 291. If the +12VDC supply is short circuited to the terminal "TI", the maximum short circuit current is maintained at the value of the saturation current of the transistor 279 and the output voltage of the +15VDC supply will be reduced to approximately 3VDC.
- first terminating means 293 having suitable terminals 47 as, for example, spade lugs for wiring attachment.
- the terminating means 293 preferably incorporates a travel adjustment potentiometer 235 for preselecting a second angular position of the output shaft 33. It is convenient to arbitrarily designate the first angular position as being at 0° and the potentiometer 235 permits the selection of a second angular position within a predetermined range of angular positions.
- the resulting difference between the first and second positions defines the magnitude of the arc segment through which the output shaft 33 may be turned as the command signal changes from zero to full value.
- the predetermined range of angular positions is between 65 and 270 . Selection of a second angular position of 100°, for example, will permit the shaft 33 to rotate between the positions at 0° and 100° over the full range of the command signal.
- the family of circuits comprising the first control circuit 227, the second control circuit 239 and the terminating means 293 as well as the circuits of other embodiments described hereinafter may be constructed using individually wired components or, in the alternative, may each be assembled to printed circuit boards.
- control circuits 227, 229 and the terminating means 293 of the first preferred embodiment are each fabricated as discrete printed circuit boards configured such that the board 251 of first control circuit 227 may be received in a first location 295, the board 297 of the second control circuit 239 in a second location 299 and the board 301 of the terminating means 293 in a third location 303, all as seen in FIGURE 2.
- connections between the boards 251, 297, 301 may be readily accomplished using plug-in connectors.
- the first control circuit board 251 of FIGURE 18 embodies the schematic diagram of that same circuit 227 as shown in FIGURE 17.
- the board 251 includes a first group 305 of upwardly extending, parallel, spaced-apart terminating studs for connection to the terminating means board 301 and a second group 307 and third group 309 of similarly arranged terminating studs for connection to the second control circuit board 297.
- the first terminating means board 301 includes a first group 311 of upwardly extending, generally parallel, spaced-apart terminating ferrules of generally tubular construction, each having an opening therethrough sized to slidably engage a correspondingly positioned stud of the first group 305 for electrical conduction therebetween.
- a second control circuit board 297 includes a second group 313 and a third group 315 of terminating ferrules sized and located to slidably engage correspondingly positioned studs of the second group 307 and the third group 309 for electrical conduction therebetween.
- a plurality of spaced apart terminals 47 embodied as spade lugs are provided thereon and are formed to extend generally normal to the surface of the board 301.
- annular insulating disk As best seen in FIGURE 2, an annular insulating disk
- EA _ OMH_ 317 is disposed between the board 251 and the shoulder surrounding the third pocket 115 for the prevention of electrical short circuits at the inward side of the board 251.
- an L-shaped support bracket 319 is formed to engage the upper extremity of the board 297 for support while an insulating barrier 321 is interposed between the bracket 319 and the board 297 for electrically insulative protection of the latter.
- the HVAC system may be configured to provide an economizer function by coupling the system to a device sensitive to the enthalpy, i.e., sensible heat of the outside ambient air.
- a device sensitive to the enthalpy i.e., sensible heat of the outside ambient air.
- the HVAC system is selectively disabled so that no energy is expended for cooling of air introduced into the conditioned space and the system relies instead upon the then-existing ambient air characteristics to maintain human comfort.
- the electric control means of the second embodiment is shown to include a third circuit 323 and a second terminating means 325 used in place of the second circuit 239 and the first terminating means 293, respectively, of the first embodiment.
- the third circuit 323 includes, in addition to the basic triggering and signal shift circuitry shown in FIGURE 19, a comparator means 327 for receiving a sensor signal representative of the actual temperature within a mixed air space of the air delivery system and for receiving a setpoint signal representative of the desired temperature within that space.
- the comparator means 327 selectively generates an error signal based upon a comparison of those signals for controllably positioning the actuator output shaft 33.
- the circuit- 323 also includes a position adjustment means 329 for setting a minimum angular position of the output shaft 33 to provide a minimum damper opening.
- the third circuit 323 is preferably embodied in a third circuit board assembly 331 comprising a third circuit board 333 and a fourth circuit board 335 constructed and arranged to be received in the actuator enclosure 11 at the second location 299 and the fourth location 337 respectively, with connection therebetween by a multiconductor ribbon type harness (not shown) .
- the electric control means of the second embodiment also includes a second terminating means 325 constructed and arranged in a printed circuit board to be received in the third location 303 within the enclosure 11 in place of the board 301.
- the second terminating means 325 includes a first relay having its coil 339 connected to terminals A, B for the application of an operating voltage.
- the contacts 341 of the first relay are connected in parallel with one another and with a pair of sensor terminals SI, S2 adapted to be connected to and receive signals from an external temperature sensor.
- a potentiometer 343 is provided for selecting the desired temperature setpoint. Arrangement in this manner will permit the coil 339 of the first relay to be controllably energized by a separately provided, enthalpy-sensitive economizer controller.
- the second terminating means 325 also includes a second auxiliary relay having a coil 345 and contacts 346 which may be discretionarily used by the installer.
- the comparator means 321 includes a resistance bridge comprised of the resistors 348, 349, 350, 351 and 352 for receiving a plurality of input voltage signals and selectively generating an error signal based thereon.
- the input voltage signal representative of the temperature within the conditioned space is received at the control circuit 323 at the terminal FBO while the input voltage representative of temperature setpoint signal is received at the terminal TI. Since the resulting error signal may have a magnitude insufficiently high to be useful as a control signal, it is preferable that the comparator means 327 also include an amplifier 353 for receiving the error signal at pin 3 thereof and amplifying it with a gain adjustable by the value of the fixed resistor 355 and the variable resistor 357.
- the output voltage appearing at pin 6 of the amplifier 353 is filtered by a resistor 359 and capacitor 361 then directed to the X input terminal through the resistor 363.
- the temperature sensor which is adapted to be coupled to the terminals SI, S2 of the terminating means 325 is preferably a thermistor of the negative temperature coefficient type which exhibits a resistance inversely related to the sensed temperature. If the value of the sensed temperature declines, the resistance appearing across the terminals FBO and TI of the second terminating means 325 will increase, resulting in an increase of the voltage at pin 3 of amplifier 353 and therefore at the output pin 6 thereof.
- Rotational positioning movement of the actuator output shaft 33 will occur whenever this voltage exceeds +6VDC in the preferred embodiment and will cease when such voltage exceeds -HLOVDC. It is to be appreciated that changes in the sensed temperature will cause rotational movement of the shaft 33 only when the coil 339 is energized to open the contacts 341 connected in parallel with the sensor. If the coil 339 is de-energized by an economizing controller, the sensor is electrically shorted and the actuator shaft 33 rotates to a minimum damper opening position as determined by the value of the resistor 365. It should be understood that the electric control means of the second embodiment is
- OMPI v - typically used with actuators from which the spring return feature is omitted and the portrayal in FIGURE 10 is merely for illustrating the positioned locations 299, 337 within the enclosure 11.
- the first circuit board 251, second circuit board 29 and the board 301 embodying the first terminating means 293 are assembled within the enclosure 11 as described above.
- a preferred motor 15 may be operated at a preferred voltage of 24VAC. within a preferred range of 20-30VAC, the voltage being applied at terminals TI and T2 of the first terminating means 293 with the former being common.
- the voltage at pin 10 with respect to pin 9 is +2V. while the voltage at pin 10 with respect to TI is +12VDC.
- the potentiometer 235 is adjusted for preselecting the desired second angular position of the output shaft 33.
- an external three-wire potentiometer (not shown) is coupled between pins 9 and 10, the slide wire thereof being coupled to pin 8.
- the potentiometer is actuable by, for example, a pressure or temperature sensor or may be manually manipulated.
- an input signal having a first value is coupled between pins 10 and TI.
- a preferred controller has an output terminal coupled to pin 8 for providing an output signal thereto which ranges between 0VDC. and +2VDC.
- a controller may provide such output signals to be representative of and based upon, for example, sensed temperature, pressure or humidity and controllers as made by Johnson Controls, Inc., of Milwaukee, Wisconsin are preferred.
- an input signal having a first value having a
- _TJ OHMPI range of OVDC. to +24VDC. is coupled between pins X and TI with the former at positive polarity. In the preferred embodiment, rotation of the output shaft 33 will occur at signals within the +6VDC. to -lOVDC. range.
- the potentiometer 367 provides the same function as the potentiometer 235 of FIGURE 22 while the potentiometer 343 is used for selection of the economizing set point temperature at which mixing of outside air will occur to hold the selected temperature.
- the rotary actuator 10 shown and described herein may be configured by the use of a variety of plug-in printed circuit boards to be adapted to any one of a wide variety of HVAC applications and control strategies. Further, construction and arrangement of the actuator 10 including its printed circuit boards in the manner shown and described will permit marketing merchants to stock basic models of the actuator including spring return and non-spring return versions and readily adapt them to any one of a wide variety of applications using stocked electric controller components.
- Resistance is in ohms, 5% tolerance, l/4w. unless otherwise specified; capacitance is in microfarads, 20% tolerance.
- FIGURE 25 - see values for FIGURE 19 plus
- R201 1.35K, 5%, 2w, ww R202 10K, 20%, 2w, ww
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB08426014A GB2144589A (en) | 1983-02-25 | 1984-02-21 | Electrically-controlled rotary actuator |
NL8420046A NL8420046A (en) | 1983-02-25 | 1984-02-21 | ELECTRICALLY CONTROLLED ROTARY ACTUATOR. |
SE8405247A SE8405247L (en) | 1983-02-25 | 1984-10-19 | ELECTRICALLY CONTROLLED ROTATING MANOVER |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US06/469,929 US4482847A (en) | 1983-02-25 | 1983-02-25 | Electrically-controlled rotary actuator |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1984003371A1 true WO1984003371A1 (en) | 1984-08-30 |
Family
ID=23865593
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US1984/000233 WO1984003371A1 (en) | 1983-02-25 | 1984-02-21 | Electrically-controlled rotary actuator |
Country Status (9)
Country | Link |
---|---|
US (1) | US4482847A (en) |
EP (1) | EP0137032A1 (en) |
JP (1) | JPS60500738A (en) |
AU (1) | AU564319B2 (en) |
CA (1) | CA1251540A (en) |
DE (1) | DE3490071T1 (en) |
GB (1) | GB2144589A (en) |
NL (1) | NL8420046A (en) |
WO (1) | WO1984003371A1 (en) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4779031A (en) * | 1985-12-30 | 1988-10-18 | Intellico, Inc. | Motor system |
US5038088A (en) * | 1985-12-30 | 1991-08-06 | Arends Gregory E | Stepper motor system |
GB8811650D0 (en) * | 1988-05-17 | 1988-06-22 | Econocruise Ltd | Improvements in & relating to electromagnetic actuators |
US4947068A (en) * | 1989-03-30 | 1990-08-07 | Emerson Electric Co. | Motor for whirlpool baths |
FR2688105B1 (en) * | 1992-02-28 | 1994-05-06 | Moving Magnet Technologies Sa | ELECTROMAGNETIC ROTARY ACTUATOR SINGLE-PHASE RACE BETWEEN 60 AND 120 DEGREES. |
US5306989A (en) * | 1992-05-27 | 1994-04-26 | Johnson Service Company | Electric motor brake |
JP3450074B2 (en) * | 1994-12-31 | 2003-09-22 | 帝人製機株式会社 | Control device for planetary differential reducer |
US5793131A (en) * | 1996-08-07 | 1998-08-11 | General Electric Company | Systems and apparatus for controlling energization of electric motor windings, and methods of assembling motors |
US6249100B1 (en) | 1997-07-31 | 2001-06-19 | Honeywell International Inc. | Drive circuit and method for an electric actuator with spring return |
US6548981B1 (en) * | 1999-02-10 | 2003-04-15 | Sony Corporation | Actuator |
US6369540B1 (en) * | 2000-11-21 | 2002-04-09 | Honeywell International Inc. | Bypass circuit for use in DC brush motor control |
GB0109038D0 (en) * | 2001-04-10 | 2001-05-30 | Lucas Industries Ltd | Actuator apparatus including a marker device |
JP4003754B2 (en) * | 2004-03-26 | 2007-11-07 | 株式会社デンソー | Reluctance motor rotor angle detector |
ATE502427T1 (en) * | 2005-07-06 | 2011-04-15 | Graaf B V V D | DRUM MOTOR DRIVE AND USE THEREOF |
CN108696057B (en) * | 2017-04-12 | 2021-06-25 | 德昌电机(深圳)有限公司 | Motor and electric equipment with same |
DE102018203998A1 (en) * | 2018-03-15 | 2019-09-19 | Mahle Lnternational Gmbh | Actuation device for the mechanical actuation of a component |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1903230A (en) * | 1929-07-13 | 1933-03-28 | Howard D Colman | Electric valve operator |
DE1438923A1 (en) * | 1963-09-28 | 1969-01-02 | Bauer Eberhard Gmbh | Electromotive actuator |
FR2099422A1 (en) * | 1971-08-04 | 1972-03-17 | Emerjy | |
US3789283A (en) * | 1973-02-20 | 1974-01-29 | Honeywell Inc | Condition control reversible motor system |
DE2408627A1 (en) * | 1973-02-20 | 1974-08-22 | Mallory & Co Inc P R | CLUTCH AND GEAR FOR DRIVE EQUIPMENT, SUCH AS SYNCHRONOUS MOTORS OR THE SAME |
FR2216503A1 (en) * | 1973-02-05 | 1974-08-30 | Worcester Controls Corp | |
FR2269138A1 (en) * | 1974-04-29 | 1975-11-21 | British Petroleum Co | |
US4087728A (en) * | 1976-11-24 | 1978-05-02 | Honeywell Inc. | Adjustable stroke electric motor using stroke adjusting linkage means |
FR2445648A1 (en) * | 1978-12-28 | 1980-07-25 | Tlv Co Ltd | Electric motor driving gear - includes gear train for power transmission and detector switch and motor current control switch |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3609498A (en) * | 1969-12-05 | 1971-09-28 | Intercontinental Dynamics Corp | Converter for positioning a continuously rotatable shaft utilizing cyclic digital information |
US3736486A (en) * | 1972-03-17 | 1973-05-29 | Teletronics Int Inc | Servo control system |
DE2717178C3 (en) * | 1977-04-19 | 1979-12-06 | Eduard 7303 Neuhausen Hermle | Electronic rear derailleur |
US4190792A (en) * | 1978-03-09 | 1980-02-26 | Vincent Chan | Positioning control system |
US4289996A (en) * | 1978-08-29 | 1981-09-15 | Frazer Nash Limited | Actuators |
-
1983
- 1983-02-25 US US06/469,929 patent/US4482847A/en not_active Expired - Lifetime
-
1984
- 1984-02-21 WO PCT/US1984/000233 patent/WO1984003371A1/en not_active Application Discontinuation
- 1984-02-21 EP EP84901158A patent/EP0137032A1/en not_active Withdrawn
- 1984-02-21 GB GB08426014A patent/GB2144589A/en not_active Withdrawn
- 1984-02-21 DE DE19843490071 patent/DE3490071T1/en not_active Withdrawn
- 1984-02-21 NL NL8420046A patent/NL8420046A/en unknown
- 1984-02-21 AU AU25786/84A patent/AU564319B2/en not_active Ceased
- 1984-02-21 JP JP59501107A patent/JPS60500738A/en active Pending
- 1984-02-23 CA CA000448180A patent/CA1251540A/en not_active Expired
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1903230A (en) * | 1929-07-13 | 1933-03-28 | Howard D Colman | Electric valve operator |
DE1438923A1 (en) * | 1963-09-28 | 1969-01-02 | Bauer Eberhard Gmbh | Electromotive actuator |
FR2099422A1 (en) * | 1971-08-04 | 1972-03-17 | Emerjy | |
FR2216503A1 (en) * | 1973-02-05 | 1974-08-30 | Worcester Controls Corp | |
US3789283A (en) * | 1973-02-20 | 1974-01-29 | Honeywell Inc | Condition control reversible motor system |
DE2408627A1 (en) * | 1973-02-20 | 1974-08-22 | Mallory & Co Inc P R | CLUTCH AND GEAR FOR DRIVE EQUIPMENT, SUCH AS SYNCHRONOUS MOTORS OR THE SAME |
FR2269138A1 (en) * | 1974-04-29 | 1975-11-21 | British Petroleum Co | |
US4087728A (en) * | 1976-11-24 | 1978-05-02 | Honeywell Inc. | Adjustable stroke electric motor using stroke adjusting linkage means |
FR2445648A1 (en) * | 1978-12-28 | 1980-07-25 | Tlv Co Ltd | Electric motor driving gear - includes gear train for power transmission and detector switch and motor current control switch |
Also Published As
Publication number | Publication date |
---|---|
AU564319B2 (en) | 1987-08-06 |
DE3490071T1 (en) | 1985-06-27 |
GB8426014D0 (en) | 1984-11-21 |
NL8420046A (en) | 1985-01-02 |
GB2144589A (en) | 1985-03-06 |
JPS60500738A (en) | 1985-05-16 |
US4482847A (en) | 1984-11-13 |
AU2578684A (en) | 1984-09-10 |
EP0137032A1 (en) | 1985-04-17 |
CA1251540A (en) | 1989-03-21 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
AU564319B2 (en) | Electrically-controlled rotary actuator | |
US4584511A (en) | Controllable rotary actuator | |
Montgomery et al. | Fundamentals of HVAC control systems | |
AU559860B2 (en) | Controllable rotary actuator | |
US4712441A (en) | Position controlled linear actuator | |
US4858481A (en) | Position controlled linear actuator | |
US5592989A (en) | Electronic thermostat having high and low voltage control capability | |
US20070170385A1 (en) | Reduction gearing for an electric actuator | |
US5586867A (en) | Direct mounted fan apparatus | |
US4087728A (en) | Adjustable stroke electric motor using stroke adjusting linkage means | |
US5990586A (en) | Multi-actuator having position controller | |
US3825182A (en) | Control devices for dampers and the like | |
US3743182A (en) | Temperature sensitive controls for air conditioning systems | |
US4000663A (en) | Damper actuator | |
JP2005204498A (en) | Gear box control device especially for cars | |
US2112218A (en) | Motorized control system | |
US6957801B2 (en) | Valve having an integrated actuator assembly | |
US1877605A (en) | Opposed motor control system | |
CA1092217A (en) | Electronic reversible motor operated valve assembly | |
US3255636A (en) | Control mechanism | |
JPH01275977A (en) | Proportional flow control valve and indoor temperature control system | |
JPH1061809A (en) | Motor-driven valve actuator | |
JPH01250681A (en) | Electric ball valve | |
EP1463877A1 (en) | A pump/valve assembly and a cooling circuit containing such an assembly | |
LINCOLN | 1'10E/NASA C (" TR^ A OR DOE/N! ASA CR-150867 REPORT |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Designated state(s): AU CH DE GB JP NL SE |
|
AL | Designated countries for regional patents |
Designated state(s): BE FR |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1984901158 Country of ref document: EP |
|
WWP | Wipo information: published in national office |
Ref document number: 1984901158 Country of ref document: EP |
|
RET | De translation (de og part 6b) |
Ref document number: 3490071 Country of ref document: DE Date of ref document: 19850627 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 3490071 Country of ref document: DE |
|
WWW | Wipo information: withdrawn in national office |
Ref document number: 1984901158 Country of ref document: EP |