US3782121A - Actuator apparatus - Google Patents

Actuator apparatus Download PDF

Info

Publication number
US3782121A
US3782121A US00248942A US3782121DA US3782121A US 3782121 A US3782121 A US 3782121A US 00248942 A US00248942 A US 00248942A US 3782121D A US3782121D A US 3782121DA US 3782121 A US3782121 A US 3782121A
Authority
US
United States
Prior art keywords
chamber
piston
casing
piston member
medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00248942A
Other languages
English (en)
Inventor
L Marcoux
P Berg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Texas Instruments Inc
Original Assignee
Texas Instruments Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Texas Instruments Inc filed Critical Texas Instruments Inc
Application granted granted Critical
Publication of US3782121A publication Critical patent/US3782121A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • G—PHYSICS
    • G12—INSTRUMENT DETAILS
    • G12B—CONSTRUCTIONAL DETAILS OF INSTRUMENTS, OR COMPARABLE DETAILS OF OTHER APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G12B1/00—Sensitive elements capable of producing movement or displacement for purposes not limited to measurement; Associated transmission mechanisms therefor

Definitions

  • An actuator for converting electrical energy into linear mechanical movement comprises a chamber containing an expandable material and a positive temperature coefficient (PTC) of resistance heater located in thermal communication with the chamber.
  • a first piston transmits force from the expandable material to an external load against the force of a first return spring.
  • the first piston moves out of a casing from a retracted position at a first stop to a protracted position at a second stop at which point continued expansion of the expandable material in one embodiment causes a second piston to separate the chamber from the heat source against the bias of a second return spring.
  • the chamber separates the thermal resistance between the heat source and the chamber greatly increases until equilibrium is obtained between heat input to the expandable medium and pressure exerted by the medium.
  • This invention relates generally to thermal actuators and more particularly to a thermal actuator for converting electrical energization into mechanical movement.
  • a thermal actuator in which a self-regulating heat generating element is disposed in thermal communication with a chamber containing a thermally expandable medium. Electrical energization of the heat generating element causes the thermally expandable medium to expand which in turn causes linear movement of a piston mounted in force receiving relation to the medium.
  • a self-regulating heat generating element provides a device in which overheating is avoided even though substantially constant electrical energization may be employed.
  • This actuator as well as other prior art actuators, is calibrated to produce a desired stroke, however, this calibrator is subject to change over the life of the device due to loss of some of the expandable medium from the chamber or by a change in volume of the chambers should it be deformed by an accidental blow. Such actuators are also subject to damage should the piston be prevented from movement by some static, external force. Further, the maxi mum temperature of the heat generating device must be chosen low enough that deterioration ofthe expandable medium is not effectedl While these characteristics do not serve as limitations for many uses of thermal actuators there are certain situations where they do become important.
  • a thermal actuator having a force applying piston is providedin which the stroke of the piston is accurately determined by mechanical stops.
  • continued expansion of the expandable medium causes the chamber containing the expandable medium to separate from the heat source against the bias of a second return spring thereby altering thermal communication from the heat source to the medium to maintain the pressure level within the desired limits.
  • Faster response time of the actuator can be obtained since a higher temperature heat source can be employed due to this separation.
  • the location of the chamber is fixed within the casing but asecond piston is driven to expand the available volume of the chamber.
  • FIG. 1 is a front elevation of a thermal actuator made in accordance with the invention
  • FIG. 2 is a top view of the actuator shown in FIG. 1;
  • FIG. 3 is a bottom view of the actuator;
  • FIG. 4 is a cross section taken on lines 44 of FIG.
  • FIG. 5 is a graph of log resistance versus temperature for a heating element used in the actuator
  • FIG. 6 is a graph of volumetric expansion versus temperature for a thermally expandable material useful in the actuator of the present invention.
  • FIG. 7 is a simplified cross section similar to FIG. 4 showing the actuator in the unactuated position
  • FIG. 8 is a view similar to FIG. 7 showing an intermediate state of actuation in which the force applying piston has just reached its full stroke;
  • FIG. 9 is a view similar to FIGS. 7 and 8 but showing the device fully actuated
  • FIG. 10 is a view similar to FIG. 7 showing means to adjust the length of stroke of the actuator piston
  • FIG. 11 is a view similar to FIG. 8 showing an alternative embodiment in an intermediate state of actuation in which the force applying piston has just reached its full stroke;
  • FIG. 12 is a view similar to FIG. 11 showing the actuator of the alternative embodiment in its fully actuated state
  • FIG. 13 shows the actuator mounted on a support
  • FIG. 14 shows an alternative mounting for the actuator.
  • a thermal actuator is designated generally by reference numeral 10.
  • An outer casing of electrically insulative material such as electrically insulative phenolic resin is shown formed of two identical halves 12, 14 split longitudinally and define a generally cylindrical shaped cavity 16 therein. Apertures l8 and 20 are provided in each casing half which receive rivets (not shown) to fix the halves 12, 14 together.
  • a pin 22 is formed in the casing half for insertion in a mating depression 24 of a like casing half to insure proper alignment of the two halves.
  • piston member 26 Contained in cavity 16 is a piston member 26, generally cylindrical in configuration, which conveniently may be molded out of phenolic material.
  • Piston member 26 is formed with an integral outwardly extending radial flange 28 on one end thereof the periphery of which is closely received in cavity 16.
  • a coil spring 30 is placed about piston member 26 between flange 28 and top wall portion 32 of the casing so that piston member 26 is adapted to slide within the cavity against the bias of spring 30.
  • Piston member 26 is formed with a reduced diameter rod portion 34 which forms an annular shoulder 36 with the main body of member 26 which serves to limit outward movement of member 26 by abutment with top wall 32 of the casing.
  • Aperture 38 in top wall portion 32 slidingly receives reduced diameter portion 34.
  • annular seat 40 against which bottom surface 44 of flange 28 is biased by spring 30.
  • Piston member 26 is provided with a bore 42 communicating with bottom surface 44 and is formed with an integrally formed downwardly extending rod 46.
  • the depth of bore 42 is chosen so that it exceeds the length of the piston stroke.
  • a chamber 48 is formed of a thermally conductive material such as brass and has a first body portion 50 joined to a second open ended sleeve portion 52 by a truncated portion 54.
  • Sleeve portion 52 extends into bore 42 of piston member 26 and preferably fits closely to the side wall of bore 42 to serve as guiding means to keep the parts aligned and prevent any tendency of wobbling.
  • An outwardly extending flange 56 is formed on the free end of body portion 50 to facilitate crimping attachment of base 58 as shown at 60.
  • Base 50 is provided with an open ended tubular sleeve 62 which extends inwardly into the chamber.
  • a thermally expandable medium 64 of a type to be more fully described below is contained within chamber 48.
  • a first floating piston head 66 is slidingly received within sleeve 52 while a second floating piston head 68 is slidingly received in sleeve 62.
  • Floating piston heads 66, 68 are provided with sea] seating grooves 70, 72 respectively which receive therein suitable O- ring seals 74, 76 respectively.
  • Seals 74, 76 are formed of relatively flexible rubber like material capable of continuous high temperature operation such as a fluoroelastomer material.
  • a second coil return spring 78 is received between crimped flange portion 60 of body 50 and a shoulder 80 formed in the casing which spring biases chamber 48 toward the bottom of the casing against a force receiving, thermally conductive plate 82.
  • Terminals 84, 86 extend through apertures provided in the bottom wall 88 of the casing.
  • Terminal 84 is preferably formed with a laterally extending circular plate 90 seated on shoulder 98 formed in the casing and to which is bonded a wafer 92 of material having a positive temperature coefficient of resistance (PTC).
  • PTC positive temperature coefficient of resistance
  • the wafer is provided with metalized contact surfaces on both opposite faces, one face may be either soldered to plate 90 or cemented thereto as by electrically conductive silver epoxy.
  • Terminal 86 is formed with a laterally extending platform 94. Electrically conductive terminal spring 96 extends between the second face of wafer 92 and platform 94.
  • Wafer 92 is preferably composed of material having a positive temperature coefficient of resistance (PTC) with a steep slope at temperatures above an anomaly so that upon electrical energization it will self regulate at a chosen temperature.
  • PTC positive temperature coefficient of resistance
  • An example of suitable material is semiconducting barium titanate ceramic doped with lanthanum such as Ba La TiO
  • lanthanum such as Ba La TiO
  • FIG. 5 the log resistance versus temperature curve 100 of a PTC wafer useful in the invention is shown in FIG. 5. It will be noted that at temperatures below an anomaly temperature of approximately 120C. the resistance is essentially constant, however, above the anomaly temperature the resistance abruptly increases by several orders of magnitude.
  • An increase in input voltage initially increases input power to the wafer causing a small increase in operating temperature which causes a larger increase in resistance which in turn drives the input power level back toward its original operating point.
  • a decrease in input voltage initially decreases input power causing a small decrease in operating temperature which causes a larger decrease in resistance which in turn drives the input power level back up to its operating point.
  • FIG. 6 shows the volume expansion versus temperature curve 102 for one such material which is a processed paraffin wax having a narrow molecular weight distribution. Such material has a volumetric expansion coefficient which is much greater in the solid to liquid phase change range than either the solid or the liquid expansion coefficient. The wax maintains its expansion properties indefinitely and they are virtually independent of pressure.
  • the particular material chosen for medium 64 is such that it has a phase change temperature range above the highest ambient expected during operation of the actuator since it is desired that piston movement take place during the high expansion phase change of the medium.
  • the medium represented in FIG. 6 has a phase change range from to C. and is particularly useful in the invention with a PTC wafer having an anomaly temperature higher than the range, e.g. C. as will be explained below.
  • actuator 10 Operation of actuator 10 will be explained with particular reference to FIGS. 7-9 which are somewhat simplified facilitate understanding of the operation.
  • FIG. 7 depicts actuator 10 in the unenergized or unactuated condition as shown in FIG. 4.
  • heat source 92 Upon energization of heat source 92 by impressing a voltage thereacross through terminals 84, 86 the temperature of the PT C wafer quickly reaches its operating point T, (FIG. 5) and heat is conducted to the expandable medium 64 through brass chamber 48.
  • T operating point
  • sleeve 62 which projects into the chamber enhances heat transfer from the heat source to the medium 64.
  • the phase change begins to occur and forces piston member 26 outwardly against the bias of spring 30 until stop surface 36 of piston member 26 abuts wall 32 of the chamber thereby limiting the piston stroke, as seen in FIG. 8.
  • Separation of chamber 48 from the heat source also permits use of a PTC wafer with a higher anomaly point than would otherwise be possible without driving the expandable medium to excessive temperature since the heat input to the medium is reduced by the separation limiting the temperature rise of the medium.
  • FIGS. 11 and 12 Another embodiment is shown in FIGS. 11 and 12, FIG. 11 showing an actuator just after piston member 26 has reached its full protracted position and FIG. 12 showing the actuator fully actuated and in equilibrium.
  • This embodiment is particularly useful when it is desired to have a longer cool down time after deenergization of the actuator. For instance, when used for a locking mechanism for a high temperature over such as a pyrolytic self-cleaning oven when a positive time delay is desired to permit sufficient cooling of the oven interior before opening of the oven can be effected even if there is a loss of electrical power.
  • actuator has a modified expandable medium chamber 112. Chamber 112 is fixed in the casing by any appropriate means and has a floating piston head 114 which is biased against seat 116 by spring 118.
  • this actuator is identical to those of actuator 10 and operation is the same except that instead of effecting an equilibrium by means of reducing heat transfer by separation of the chamber from the heat source the volume of the chamber is allowed to increase by depression of piston head 114 against the bias of return spring 118, as seen in FIG. 12.
  • the temperature of the medium will be maintained at a higher level even after deenergization of the actuator due to its close thermal coupling with the heat source during the entire cycle.
  • This embodiment is also particularly useful when the actuator is to be used in exceptionally high ambient temperature environments, as in an engine compartment of an automobile. Depression of piston head 114 increases the volume available for the expanding wax significantly more than in the previous embodiment in which the volume increase in sleeve portion piston 62 is partly offset by the volume decrease in sleeve more volume 52. Further, if it is desired'to provide even morevolume available for the expanding wax the diameter of the sleeve 52 and hence also its bore can be increased.
  • FIG. 13 shows actuator 10 on a support 130.
  • a plurality of grooves 132 separated by lands 134 are provided around the periphery of the casing adapted to receive crescent rings 136 to lock the actuator in place.
  • the distance the actuator projects through the support may be adjusted by locating the actuator so that any land 134 is aligned with support 130.
  • actuator 10 may be received in an aperture of bracket 138 as seen in FIG. 14 with shoulder 140 of the casing biased against bracket 138 and push ring 142 locking the actuator in place.
  • Actuator apparatus comprising a hollow casing defining a cavity therein;
  • a chamber having first and second force output means received in the cavity, a thermally expandable medium contained in the chamber, energizable heat source means mounted in thermal communication with the thermally expandable medium, a first piston member slidably mounted in the casing and movable relative to the casing from a retracted position to a protracted position, means coupling the first piston member to the first force output means of the chamber to cause movement of the first piston member from the retracted position to the protracted position upon sufficient expansion of the medium, a second piston member mounted in the casing for movement relative to the chamber, and means coupling the second piston member to the second force output means of the chamber to cause movement of the second piston relative to the chamber.
  • the second force output means of the chamber is formed by means defining a bore, the second piston member slidably mounted in the bore, and means biasing the piston member toward the expandable medium, the biasing means placing a given force on the second piston member which force is greater than that required to move the first piston member from the retracted to the protracted position whereby continued expansion of the medium after the first piston has moved to the protracted position will cause the second piston member to move in a direction away from the medium to increase the effective volume of the chamber.
  • the second force output means of the chamber is formed by means defining a bore, the second piston member mounted within the bore, means limiting movement of the second piston member away from the medium, the chamber slidably mounted within the cavity, means biasing the chamber in a direction generally parallel to the axis of the bore, the biasing means placing a given force on the chamber in excess of a predetermined force used for moving the first piston member from the retracted to the protracted position whereby continued expansion of the medium after the first piston has moved to the protracted position will cause the chamber to move relative to the casing.
  • An actuator according to claim 5 in which the expandable medium has a solid to liquid phase change temperature range and the heat source wafer has a anomaly temperature above which the wafer has a steeply sloped positive temperature coefficient of resistance, the anomaly temperature being higher than the solid to liquid phase change temperature range of the expandable medium.
  • An actuator comprising a casing defining a cavity therein, electrical energizing means mounted in the casing, a chamber having first and second force output means mounted in the cavity in energy receiving relationship with the electrical energy means, an expandable medium contained in the chamber, a first piston member slidingly mounted in the casing between a retracted and a protracted position, the piston member having a force receiving surface located in force receiving relation with the first force output means of the chamber, a second piston means mounted in the casing, the second piston means having a force receiving surface located in force receiving relation with the second force output means of the chamber, the second force receiving surface larger than the first force receiving surface, and means biasing the second piston means in a direction opposed to the force exerted by the expandable medium, the biasing means exerting a given force on the second piston means in excess of a predetermined force used for moving the first piston member from the retracted to the protracted position whereby the expandable medium expands upon electrical energization causing the first piston member to move from the retracted position
  • Actuator apparatus for translating electrical energy into linear mechanical movement comprising:
  • a casing defining a cavity therein, the casing having a top wall with an aperture extending therethrough into the cavity,
  • a chamber formed of thermally conductive material having first and second bores communicating with the chamber, the chamber received in the casing,
  • first piston member slidably received in the casing cavity movable between a retracted position and a protracted position, the piston member having a first force receiving surface positioned within the first bore of the chamber, first return spring means positioned in the casing cavity and biasing the first piston member toward its retracted position,
  • second piston means including a member having a second force receiving surface received in the second bore of the chamber, the second force receiving surface movable relative to the chamber, and
  • second return spring means preventing relative movement of the second force receiving surface and the chamber until a predetermined force is exerted on the first piston member.
  • the chamber has a generally cylindrical body portion having two opposite ends a first elongated sleeve portion of reduced diameter and an intermediate truncated portion joining one end of the body portion with the first sleeve portion, and a bottom wall having an aperture therein located at the second end of the body portion, the bottom wall formed with a second elongated sleeve in communication with the aperture in the bottom wall and extending into the interior of the chamber, the first sleeve defining the first bore and the second sleeve defining the second bore.
  • An actuator according to claim 10 in which the chamber is movably received in the casing cavity and is formed with an outwardly extending radial flange, a shelf is formed in the casing, the second return spring is a helical spring extending between the radial flange of the chamber and the shelf of the casing, and means is provided to limit outward movement of the second piston member.
  • An actuator according to claim 15 including first and second terminal means extending from without the casing into the casing cavity, the first terminal having a surface extending laterally across the cavity, the second terminal having a laterally extending platform within the cavity, one face of the wafer bonded to the laterally extending surface of the first terminal and an electrically conductive spring biased into electrical contact between the other face of the wafer and the platform of the second terminal.
  • the first piston member is formed with a rod portion which extends through the aperture formed in the top wall of the casing, a projecting surface is formed on the piston member and is adapted to abut an interior stop surface of the top wall to limit outward movement of the piston member, a stop shelf is formed in the casing cavity, the piston is formed with a surface adapted to abut the stop shelf to limit inward movement of the piston member whereby the piston movement is accurately determined by the distance between the two stops.
  • An actuator according to claim 19 including a spacer mounted on the rod portion of the first piston member to shorten the piston movement.
  • Actuator apparatus comprising a hollow casing defining a cavity therein;
  • a chamber having a force output means received in the cavity, a thermally expandable medium contained in the chamber, energizable heat source means mounted in thermal communication with the thermally expandable medium, a piston member slidably mounted in the casing and movable relative to the casing from a retracted position to a protracted position, means coupling the piston member to the force output means of the chamber to cause movement of the piston member from the retracted position to the protracted position upon sufficient expansion of the medium, and means for moving the chamber relative the heat source means to decrease heat input to the medium when the piston moves to the protracted position.

Landscapes

  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
US00248942A 1972-05-01 1972-05-01 Actuator apparatus Expired - Lifetime US3782121A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US24894272A 1972-05-01 1972-05-01

Publications (1)

Publication Number Publication Date
US3782121A true US3782121A (en) 1974-01-01

Family

ID=22941363

Family Applications (1)

Application Number Title Priority Date Filing Date
US00248942A Expired - Lifetime US3782121A (en) 1972-05-01 1972-05-01 Actuator apparatus

Country Status (15)

Country Link
US (1) US3782121A (de)
JP (1) JPS5234697B2 (de)
AR (1) AR203534A1 (de)
AU (1) AU5529273A (de)
CA (1) CA981916A (de)
DD (1) DD105097A5 (de)
DE (2) DE7316296U (de)
ES (1) ES414296A1 (de)
FR (1) FR2182876B1 (de)
GB (1) GB1422140A (de)
IT (1) IT974886B (de)
NL (1) NL7306036A (de)
PL (1) PL87690B1 (de)
SE (1) SE401720B (de)
SU (1) SU519152A3 (de)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3911680A (en) * 1974-11-22 1975-10-14 Gen Housewares Corp Intermittent bimetallic-operated motor
US4104507A (en) * 1977-01-14 1978-08-01 Design & Manufacturing Corporation PTC heater for enhancing thermal actuator response
US4222239A (en) * 1976-09-30 1980-09-16 Masataka Negishi Heat engine
US4311653A (en) * 1977-11-10 1982-01-19 Texas Instruments Incorporated Fast idle carburetor system
US4343154A (en) * 1977-11-28 1982-08-10 Jarret Jean M Motive device for converting a variation in temperature into mechanical energy
US4699235A (en) * 1986-03-24 1987-10-13 General Motors Corporation Linear actuator control system for split axle drive mechanism
US5062175A (en) * 1990-05-16 1991-11-05 General Motors Corporation Windshield wiper with adjustable wiping pressure
US5429221A (en) * 1993-06-07 1995-07-04 Ford Motor Company All-wheel drive free-wheel mechanism for a motor vehicle
US6121588A (en) * 1997-11-17 2000-09-19 Eltek S.P.A. Thermal actuation device
US6336541B1 (en) * 1999-01-08 2002-01-08 Eltek S.P.A. Actuation device having improved working speed
US20020033032A1 (en) * 2000-09-20 2002-03-21 Hong-Yeol Lee Drainage control device for washing machines
WO2003081052A1 (en) * 2002-03-23 2003-10-02 Starbridge Systems Limited Macromechanical components
EP1394408A2 (de) * 2002-08-07 2004-03-03 ELTEK S.p.A. Elektrothermische Betätigungseinrichtung
US20040074894A1 (en) * 2002-10-22 2004-04-22 Santanam Chandran Bhala Variable flow thermostat and method for variably controlling engine temperature
US20080265044A1 (en) * 2004-10-18 2008-10-30 Oliver Maier Fuel cell coolant temperature determination method
US20090182165A1 (en) * 2006-04-12 2009-07-16 Harry Kaiser Process for the Preparation of Carbonylation Products

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2625561B2 (de) * 1976-06-05 1980-02-21 Behr-Thomson Dehnstoffregler Gmbh, 7014 Kornwestheim Regelkreis zur Durchflußregelung eines flüssigen oder gasförmigen Mediums
DE2731913A1 (de) * 1977-07-14 1979-02-01 Daimler Benz Ag Leerlaufeinstellvorrichtung fuer einspritzpumpen, insbesondere diesel-einspritzpumpen
DE2908694C2 (de) * 1979-03-06 1985-04-04 Michaelis, Frobert, Dipl.-Ing., 6000 Frankfurt Solarthermisch betriebene Wasserpumpe
JPS5924795A (ja) * 1982-08-02 1984-02-08 長谷川香料株式会社 脱テルペン化精油の製法
ES2333194B1 (es) * 2008-04-21 2011-01-31 Arquimea Ingenieria, S.L. Actuador de material con memoria de forma.

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3430440A (en) * 1966-12-23 1969-03-04 Renriden Corp Electro-thermal actuator
US3431726A (en) * 1966-07-02 1969-03-11 Danfoss As Servomotor

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3431726A (en) * 1966-07-02 1969-03-11 Danfoss As Servomotor
US3430440A (en) * 1966-12-23 1969-03-04 Renriden Corp Electro-thermal actuator

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3911680A (en) * 1974-11-22 1975-10-14 Gen Housewares Corp Intermittent bimetallic-operated motor
US4222239A (en) * 1976-09-30 1980-09-16 Masataka Negishi Heat engine
US4104507A (en) * 1977-01-14 1978-08-01 Design & Manufacturing Corporation PTC heater for enhancing thermal actuator response
US4311653A (en) * 1977-11-10 1982-01-19 Texas Instruments Incorporated Fast idle carburetor system
US4343154A (en) * 1977-11-28 1982-08-10 Jarret Jean M Motive device for converting a variation in temperature into mechanical energy
US4699235A (en) * 1986-03-24 1987-10-13 General Motors Corporation Linear actuator control system for split axle drive mechanism
US5062175A (en) * 1990-05-16 1991-11-05 General Motors Corporation Windshield wiper with adjustable wiping pressure
US5429221A (en) * 1993-06-07 1995-07-04 Ford Motor Company All-wheel drive free-wheel mechanism for a motor vehicle
US6121588A (en) * 1997-11-17 2000-09-19 Eltek S.P.A. Thermal actuation device
US6336541B1 (en) * 1999-01-08 2002-01-08 Eltek S.P.A. Actuation device having improved working speed
US20020033032A1 (en) * 2000-09-20 2002-03-21 Hong-Yeol Lee Drainage control device for washing machines
US6931892B2 (en) * 2000-09-20 2005-08-23 Samsung Electronics Co., Ltd. Drainage control device for washing machines
WO2003081052A1 (en) * 2002-03-23 2003-10-02 Starbridge Systems Limited Macromechanical components
US20060044084A1 (en) * 2002-03-23 2006-03-02 Joseph Cefai Macromechanical components
EP1394408A2 (de) * 2002-08-07 2004-03-03 ELTEK S.p.A. Elektrothermische Betätigungseinrichtung
EP1394408A3 (de) * 2002-08-07 2006-08-30 ELTEK S.p.A. Elektrothermische Betätigungseinrichtung
US20040074894A1 (en) * 2002-10-22 2004-04-22 Santanam Chandran Bhala Variable flow thermostat and method for variably controlling engine temperature
US6867395B2 (en) * 2002-10-22 2005-03-15 General Motors Corporation Variable flow thermostat and method for variably controlling engine temperature
US20080265044A1 (en) * 2004-10-18 2008-10-30 Oliver Maier Fuel cell coolant temperature determination method
US7455241B2 (en) * 2004-10-18 2008-11-25 General Motors Corporation Fuel cell coolant temperature determination method
US20090182165A1 (en) * 2006-04-12 2009-07-16 Harry Kaiser Process for the Preparation of Carbonylation Products

Also Published As

Publication number Publication date
FR2182876B1 (de) 1976-11-05
IT974886B (it) 1974-07-10
GB1422140A (en) 1976-01-21
CA981916A (en) 1976-01-20
SU519152A3 (ru) 1976-06-25
PL87690B1 (de) 1976-07-31
JPS4925339A (de) 1974-03-06
JPS5234697B2 (de) 1977-09-05
AR203534A1 (es) 1975-09-22
ES414296A1 (es) 1976-05-01
DE2321767A1 (de) 1973-11-15
FR2182876A1 (de) 1973-12-14
NL7306036A (de) 1973-11-05
DE7316296U (de) 1976-11-18
SE401720B (sv) 1978-05-22
DD105097A5 (de) 1974-04-05
AU5529273A (en) 1974-11-07

Similar Documents

Publication Publication Date Title
US3782121A (en) Actuator apparatus
US3500634A (en) Control system and actuator used therein
US3756083A (en) Thermally operated actuator device
EP2235379B1 (de) Thermische phasenumwandlung verwendender fahrwerkeinfahrverriegelungsmechanismus
US4212346A (en) Variable heat transfer device
US2990716A (en) Thermally responsive actuator
US20210293495A1 (en) Mechanism for variable thermal conductance
EP1471225B1 (de) Thermoelement
JP5273918B2 (ja) 感温式アクチュエータ
US4608870A (en) Pressure fluid reservoir
US3686857A (en) Thermal actuator
US3805528A (en) Thermal actuator
US3696611A (en) Thermal motors
US2925986A (en) Pressure operated valve
Tibbitts High-output paraffin linear motors: utilization in adaptive systems
US3173245A (en) Control apparatus
US3475904A (en) Heat motor utilizing expansible fluid for driving a piston
US6192684B1 (en) Mechanical actuator assembly
US4498491A (en) Thermo-electric valve
US5040368A (en) Electrothermally operated actuator and seal
GB1580629A (en) Electro thermal actuator
US3611713A (en) Internal heat motor
US3408725A (en) Heat motor
US2913904A (en) Mechanical transducers
US3405520A (en) Pressure seal