WO2011133166A1 - Protection antigel intégrée et soupape de décharge - Google Patents

Protection antigel intégrée et soupape de décharge Download PDF

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Publication number
WO2011133166A1
WO2011133166A1 PCT/US2010/032231 US2010032231W WO2011133166A1 WO 2011133166 A1 WO2011133166 A1 WO 2011133166A1 US 2010032231 W US2010032231 W US 2010032231W WO 2011133166 A1 WO2011133166 A1 WO 2011133166A1
Authority
WO
WIPO (PCT)
Prior art keywords
plunger
valve
bore
actuator
temperature
Prior art date
Application number
PCT/US2010/032231
Other languages
English (en)
Inventor
Kevin Lamb
Kenneth Lionello
Michael J. Nihan
Original Assignee
Rostra Vernatherm LLC
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 Rostra Vernatherm LLC filed Critical Rostra Vernatherm LLC
Priority to PCT/US2010/032231 priority Critical patent/WO2011133166A1/fr
Publication of WO2011133166A1 publication Critical patent/WO2011133166A1/fr

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Classifications

    • 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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/36—Safety valves; Equalising valves, e.g. pressure relief valves actuated in consequence of extraneous circumstances, e.g. shock, change of position
    • F16K17/38—Safety valves; Equalising valves, e.g. pressure relief valves actuated in consequence of extraneous circumstances, e.g. shock, change of position of excessive temperature
    • F16K17/383—Safety valves; Equalising valves, e.g. pressure relief valves actuated in consequence of extraneous circumstances, e.g. shock, change of position of excessive temperature the valve comprising fusible, softening or meltable elements, e.g. used as link, blocking element, seal, closure plug
    • 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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S40/00—Safety or protection arrangements of solar heat collectors; Preventing malfunction of solar heat collectors
    • F24S40/70—Preventing freezing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers

Definitions

  • the present disclosure relates to an integrated thermally actuated control valve and pressure relief valve for use in solar hot water systems.
  • the thermally actuated valve controls the opening and closing of a fluid connection to prevent freezing in a water circulation system.
  • the integrated pressure relief valve prevents excess pressure accumulation.
  • Solar hot water systems use various collectors or panels exposed to sunlight to accumulate heat energy in a working fluid circulated through the collector or panel. Some solar hot water systems circulate fresh water through the collector or panel in temperate climates where freezing temperatures are unusual. Freeze protection valves are employed in fresh water solar systems to prevent freeze damage to the collectors. Conservation of fresh water resources is important wherever such systems are used, so limiting the amount of flow necessary to prevent freeze damage to a minimum is a priority.
  • Typical solar hot water systems include a pressure relief valve to bleed off pressure in excess of a predetermined amount to prevent system damage.
  • the pressure relief valve is separate from and in addition to the freeze protection valve.
  • Wax motors have been employed as actuators for valves employed to prevent fluid sources from freezing when the temperature drops. Such valves are designed to open or close in response to a predetermined change in temperature. Wax motors require no external power source, are reliable, extremely compact and powerful for their size.
  • Wax motors typically include a housing having a chamber filled with thermally responsive wax contained beneath a flexible diaphragm.
  • the wax expands as temperature increases, exerting force on the diaphragm and on a reciprocating piston disposed on the other side of the diaphragm. Movement of the piston is controlled by a guide extending from the actuator housing.
  • the wax motor is constructed such that known changes in temperature produce predetermined axial movement of the piston with respect to the housing.
  • Wax motor-actuated freeze protection valves where the piston is seated against a stop and the housing moves in response to changes in temperature.
  • the housing carries a poppet that fits in a seat to control fluid flow.
  • a return spring biases the housing and poppet away from the seat.
  • the actuator exerts a force on the piston which moves the housing and poppet toward the seat against the bias of the return spring.
  • a predetermined temperature typically above approximately 35°F, the force generated by the wax motor overcomes that of the return spring so that the poppet reaches the seat and the system is closed.
  • valves of this type incorporate a poppet sub-assembly which accommodates actuator movement while maintaining the poppet in contact with the seat.
  • the poppet sub-assembly includes a poppet retainer and poppet spring which allow the poppet to move independently of the actuator housing while the valve is closed. The retainer limits movement of the poppet toward the seat and the poppet spring defines the pressure exerted by the poppet on the seat.
  • the poppet and seat remain stationary and sealed while the actuator housing moves in response to changes in temperature.
  • the necessity for a poppet sub-assembly complicates both valve assembly and operation.
  • the disclosure relates to a thermally actuated freeze protection valve of simplified construction and enhanced functionality.
  • a housing defines an inlet, outlet and longitudinal cavity which houses a wax-filled actuator.
  • a fluid flow channel connects the cavity and outlet.
  • the actuator body includes a cup defining a wax reservoir and a guide for controlling axial movement of the piston.
  • the actuator piston is seated against the housing, with the actuator body moving in the cavity in response to temperature changes.
  • a return spring is arranged to bias the actuator body toward the piston.
  • the disclosed freeze protection valve employs a plunger and bore valve configuration.
  • the plunger integrally extends from the actuator body and carries an O-ring seal seated in a circumferential groove.
  • the disclosed plunger and bore are circular in cross- section, but are not limited to such a configuration.
  • a circumferential wall projects into the cavity from the channel to define the bore.
  • the actuator produces axial force on the piston sufficient to overcome the return spring and project the plunger and O-ring seal into the bore.
  • the bore entrance and plunger include complementary beveled surfaces to facilitate alignment and entry of the plunger and seal into the bore.
  • the O-ring seal When the plunger is inside the bore, the O-ring seal is compressed between the inside surface of the bore and the plunger. The O-ring seal is compressed in a direction perpendicular to the direction of actuator movement. The sealing compression of the O-ring seal is independent of the force generated by the actuator.
  • the plunger defines a pressure relief fluid flow path from the valve cavity to the valve outlet.
  • a pressure relief valve is arranged in the plunger and is responsive to pressure in the valve.
  • the pressure relief valve opens to relieve pressure above a pre- determined level.
  • the thermally actuated valve and the pressure relief valve are coaxial and employ a common outlet.
  • the plunger and bore are configured with an axial length sufficient to accommodate movement of the actuator body at above freezing temperatures.
  • This configuration allows the actuator, plunger and seal to move in response to changes in temperatures, while the valve remains closed.
  • a predetermined temperature typically about 35°F
  • the wax in the actuator contracts, allowing the plunger and seal to axially disengage from the bore under the influence of the return spring, thus opening a fluid flow pathway between the inlet and the outlet. So long as temperatures remain below the predetermined value, the valve will remain open.
  • the disclosed valve configuration permits reciprocation of the plunger over a range of temperatures while the valve remains closed.
  • the disclosed valve configuration eliminates the need for numerous additional mechanical elements found in known freeze protection valves.
  • Figure 1 is a longitudinal sectional view through a first embodiment of a freeze protection valve according to aspects of the present disclosure
  • Figure 2 is an exploded preassembly sectional view of the freeze protection valve of Figure 1;
  • Figure 3 is a schematic diagram of a pump system with the freeze protection valve of Figures 1-2 installed on the return side;
  • Figure 4 is a longitudinal sectional view through the freeze protection valve of claims 1-2 illustrating the direction of actuation force Fi, return spring force F 2 , actuation range of movement ⁇ and range of actuator movement at greater than freezing temperatures ⁇ 2 ;
  • Figure 5 is a graphical presentation of actuator travel with respect to temperature change illustrating aspects of the disclosed freeze protection valve.
  • the freeze protection valve 10 has a housing 12 which includes an inlet 14, an actuator cavity 26 and an outlet 18.
  • the housing 12 has a relatively L-shaped side profile, but is not limited to such a configuration.
  • the housing 12 includes an inlet 14 which defines a fluid entry flow path 16 communicating with the actuator cavity 26 and an outlet 18 which defines a fluid discharge flow path 20.
  • the inlet 14 and outlet 18 may include threaded surfaces to facilitate integration of the valve 10 into fluid circulation systems.
  • the disclosed embodiment also includes a filter or screen 15 positioned at the inlet 14 to prevent entry of particulates that may interfere with valve function.
  • the disclosed freeze protection valve 10 features a housing 12 assembled from upper and lower portions, 34 and 36, respectively.
  • the lower portion 36 has a projection 38 with a threaded outside surface 40.
  • the upper portion 34 has an opening 42 and internal threaded surface 44 complementary to the projection 38 and external threaded surface 40 of the lower portion 36.
  • the upper housing portion 34 is sealed to the lower housing portion 36 by an O-ring 46 arranged and compressed between radially opposed surfaces of the upper and lower portions 34, 36 as shown in Figure 1.
  • the upper and lower housing portions 34, 36 are molded from plastic formulated to withstand outdoor temperature extremes and long-term exposure to UV from sunlight. Suitable plastic formulations are commercially available.
  • the connection between the housing upper and lower portions 34, 36 may alternatively be an adhesive bond, a sonic weld or other suitable method of joining.
  • a wax- filled actuator 50 disposed within the cavity 26 is a wax- filled actuator 50
  • the actuator 50 includes a body 51 which defines a cup 53, and a guide 58 for controlling axial movement of a piston 60 relative to the body 51.
  • the actuator cup 53 contains a reservoir of wax material 52 which expands and contracts in response to temperature changes in a known manner.
  • a flexible diaphragm 54 is positioned within the actuator body 51 to retain the wax 52 within the cup 53 and transmit force from the wax 52 to the piston 60, which results in axial movement of the piston 60 relative to the actuator body 51.
  • the guide 58 and cup 53 are constructed of brass, while the piston is stainless steel.
  • Housing portion 34 includes two coaxial bores 63, 65 arranged to receive the guide 58 and the end of the piston 60, respectively.
  • the piston 60 remains in fixed position with respect to the housing 12, while the guide 58 reciprocates in the bore 63.
  • the guide 58 includes a circumferential groove 59 which carries an O-ring seal 61 which is compressed between the inside surface of the bore 63 and the guide 58 to prevent fluid penetration into the area behind the guide 58. Preventing fluid from getting behind the guide lessens the chance of corrosion on the guide 58 or piston 60.
  • the sliding relationship between the guide 58, O-ring seal 61 and bore 63 serve to control axial movement of the actuator body 51 with respect to the housing 12.
  • the lower housing portion 36 includes coaxial bores 73, 74. Bore 73 surrounds a majority of the actuator chamber 26 inside the valve 10. Bore 74 defines the outlet 18 and receives the forward end of the actuator 50, described in greater detail below.
  • the actuator 50 shown in Figures 1 and 2 has a shoulder 56 projecting outwardly from the body 51.
  • a return member 62 is engaged with the actuator body 51 at the shoulder 56 and biases the body 51 away from the outlet 18.
  • the return member 62 is a coil spring, but other forms of bias member are compatible with the disclosed valve 10.
  • the spring's bias force is designated as F 2 in Figure 4.
  • the return spring force F 2 is opposed by force Fi generated by the wax 52 on the piston 60 seated against the housing upper portion 34 as shown in Figure 1.
  • thermally responsive wax can be formulated to expand to generate the actuation force Fi over a broad range of temperatures.
  • the body 51 of the actuator is extended axially to include a plunger 64.
  • the plunger 64 integrally extends from the actuator body 51 and carries an O-ring seal 66 seated in a circumferential groove 68.
  • Other arrangements, such as a mechanical connection between the actuator body 51 and the plunger 64 are compatible with the disclosed valve 10.
  • the bore 74, plunger 64 and seal 66 are configured with circular cross sections, though they are not limited to such a configuration.
  • the plunger 64 and seal 66 are connected to the actuator body 51 for axial movement therewith.
  • the O-ring seal 66 When inside the bore 74, the O-ring seal 66 is compressed between the inside surface of the bore 74 and the plunger 64. The O-ring seal 66 is compressed in a direction generally perpendicular to the direction of actuator movement, thus closing the fluid flow path between the inlet 14 and outlet 18 through cavity 26.
  • the sealing compression of the O-ring seal 66 is independent of the forces Fi and F 2 generated by the actuator 50 and the return member 62.
  • the thermally responsive wax 52 contracts with a falling temperature below a predetermined value and allows the return member 62 to move the plunger 64 and O-ring seal 66 away from the bore 74 defining the outlet 18.
  • the force F 2 exerted by the return member 62 on the actuator body 51 is greater than the actuation force Fi generated by the actuator 50 so the plunger 64 and O-ring seal 66 are withdrawn from the bore 74, opening the valve so fluid flows between the inlet 14 and outlet 18 through the cavity 26.
  • an O-ring seal is illustrated, other sealing configurations between the plunger 64 and bore 74 are compatible with the disclosed valve 10.
  • the disclosed valve 10 will spend most of its working life in the closed position, with the plunger 64 and seal 66 received in the bore 74 to prevent fluid flow through the valve.
  • the actuator contains a wax material 52 which changes state from a liquid (expanded) to a crystalline solid (contracted) in response to a pre-determined reduction in temperature.
  • the wax 52 goes through a reverse transition from crystalline solid (contracted) to liquid (expanded) in response to a pre-determined increase in temperature.
  • the disclosed valve 10 is constructed to open as temperatures fall through the range from about 36°F to 32°F, with the wax changing state from liquid (expanded) to solid (contracted).
  • the wax 52 occupies less space within the cup 53, reducing pressure Fi on the piston 60, which allows the plunger 64 and seal 66 to withdraw from the bore under the influence of the return member 62.
  • the disclosed actuator 50 is calibrated in a manner known in the art by altering the volume of the cup to establish an actuator length at a known temperature so that the plunger 64 and seal 66 are accurately positioned relative to the bore 74.
  • the actuator 50 is calibrated so that the seal 66 leaves the bore 74 at approximately 35°F, allowing fluid to begin flowing through the valve 10.
  • the disclosed exemplary freeze protection valve 10 is configured to produce approximately .150" movement ADi of the plunger 64 and seal 66 with respect to the bore 74 between 36°F and 32°F.
  • the wax material 52 is formulated to begin its transition from liquid (expanded) to solid (contracted) when the temperature of fluid in the cavity 26 surrounding the actuator 50 is approximately 36°F and complete that transition when the temperature in the cavity is approximately 32°F.
  • the wax material 52 is formulated so that a majority of the transition and the associated movement occurs between 34°F and 32°F.
  • An exemplary embodiment of the disclosed freeze protection valve divides actuator movement as follows: 5% of actuator movement occurs between 36°F and 35°F, 10% of actuator movement occurs between 35°F and 34°F, 40% of actuator movement between 34°F and 33°F and 45% of actuator movement between 33°F and 32°F.
  • Figure 5 is a graph showing actuator movement with respect to temperature for the disclosed exemplary embodiment of the valve 10. This valve configuration regulates the flow of water through the valve, with maximum flow occurring at temperatures presenting the greatest risk of freeze damage.
  • the axial force generated by the actuator, the axial length of the actuator (movement of the plunger with respect to the bore) and the flow rate through the valve are all non-linear.
  • the valve is configured to produce the greatest flow rate and greatest rate of increase in the flow rate as temperatures decline toward 32°F.
  • the bore 74 and plunger 64 of the disclosed valve 10 are configured to accommodate at least approximately .050" of movement AD 2 of the plunger 64 and seal 66 inside the bore 74 while the valve remains closed. This configuration prevents accumulation of force within the valve due to thermal expansion at high temperatures, which movement is illustrated as AD 2 in Figure 4.
  • the seal 66 is laterally compressed between the plunger 64 and the bore 74 in a direction perpendicular to actuator movement. Sealing engagement between the plunger 64 and the bore 74 is independent of temperature while the valve is in the closed position.
  • FIG. 3 illustrates a typical installed configuration for the disclosed valve 10.
  • the valve 10 serves a freeze protection function is installed in a pump fed, fresh water solar hot water system 100 as known in the art.
  • the system 100 includes a pump 76, solar collectors 78 and storage tank 79 connected via water lines 81 and 83.
  • the valve 10 is arranged in the system 100 to allow near freezing water to drain from the solar collectors 78 and be replaced by warmer water to prevent freeze damage.
  • the valve 10 is installed on the exit side of the solar collectors 78 in a location where it is exposed to the coldest ambient temperature. For optimal performance, the valve 10 is installed in an upright position.
  • the freeze protection valve 10 opens upon a drop in temperature to allow water that is near freezing to be discharged 80 and replaced with warmer water 82.
  • the coldest temperatures typically occur in the early morning hours before dawn.
  • the water circulated to replace the discharged cold water is typically coming from within the building to which the solar hot water system is attached and is therefore significantly warmer than the outside temperature.
  • the warm water expands the wax in the actuator, closing the freeze protection valve as described above.
  • the cooling, opening, warming, closing cycle repeats until the ambient temperature exceeds approximately 35°F, above which temperature the freeze protection valve remains closed.
  • the actuator body 51, plunger 64 and seal 66 move through a distance ADi with respect to the bore 74.
  • the valve 10 remains closed over a range of temperatures above about 35°F.
  • the plunger 64 and seal 66 are configured to accommodate thermal expansion of the wax and actuator components, which produce additional movement AD 2 of the actuator body 51, plunger 64 and seal 66 with respect to the bore 74.
  • the disclosed configuration of the bore 74 and its interaction with the plunger 64 and O-ring seal 66 eliminate the need for a poppet sub-assembly while retaining the functionality of the sub-assembly.
  • FIG. 3 illustrates a conventional active open loop solar domestic hot water heating system 100 including a solar collector 78, hot water storage tank 79, a pump and an automatic controller.
  • the pump 76 circulates water from the storage tank 79 to the solar collector 78 and back according to predetermined criteria.
  • the controller circulates water to accumulate hot water in the storage tank.
  • the return line 83 from the solar collector to the storage tank includes an air vent 110, a pressure relief valve 112 and a freeze protection valve (here illustrated as combination valve 10).
  • the present disclosure relates to a freeze protection valve having integrated pressure relief functionality. Integrating the pressure relief function into the freeze protection valve eliminates the need for a separate pressure relief valve.
  • the piston 60 extends from a first (guide) end of the actuator body 51 and is seated in bore 65 in fixed relationship with the housing part 34.
  • the actuator body 51 (guide 58, cup 53 and plunger 64) move relative to the piston 60 and housing 12 in response to changes in the volume of the wax 52 contained in the cup 53 and the axial force Fi exerted by the wax against the piston 60.
  • the second (plunger) end of the actuator body 51 includes an axially extending plunger 64 which carries an O-ring seal 66.
  • the second (plunger) end of the actuator body 51 defines a pressure relief fluid flow path 80 extending from the actuator cavity 26 to the outlet 18.
  • the pressure relief fluid flow path 80 includes a transverse bore 82 through the plunger in communication with an axial bore 84 extending between the transverse bore 82 and the axial (outlet) end 86 of the plunger 64.
  • a pressure relief valve 90 is assembled inside the axial bore 84 portion of the pressure relief fluid flow path 80 and exposed to the pressure in the actuator cavity 26 via the transverse bore 82.
  • the pressure relief valve 90 includes a needle 92 having a circumferential groove 94 carrying a seal 96, a bias spring 98, a spacer 100 and a retainer screw 102.
  • the retainer is a set screw which is retained in place by a pin 104 passing through the outlet end portion of the plunger 94 so the retainer screw 102 cannot rotate with respect to the plunger 64.
  • the pressure relief valve 90 is adjusted by rotation of the retainer screw 102 relative to the plunger 64 to vary the bias force against the needle 92 and seal 96.
  • the pin 104 fixes the retainer screw 102 and preserves the position of the retainer screw, spacer 100 and bias spring 98 so the adjusted bias exerted on the needle 92 and seal 96 is consistent over time.
  • the end of the axial bore 84 portion of the pressure relief fluid flow path 80 defines a conical valve seat 106.
  • a sealing end of the needle 92 has a complimentary conical configuration arranged so that the O-ring seal 96 carried by the needle 92 seals against the seat 106.
  • the bias spring 98, spacer 100 and retainer screw 102 are selected to apply a known range of pressures to the needle 92 and seal 96.
  • the disclosed pressure relief valve 90 configuration results in pressure relief valve 90 adjustable to actuate at a predetermined pressure between about 50-200 psi.
  • the pressure relief fluid flow path 80 is exposed to pressure in the valve cavity which is fluidly connected to the solar hot water system 100.
  • the pressure relief valve 90 needle 92, seal 96, bias spring 98, spacer 100, and retainer screw 102 are assembled into the plunger end of the actuator and adjusted to apply a predetermined pressure corresponding to the desired pressure relief.
  • pressure F 3 against the relief needle 92 and seal 96 overcomes the bias F 4 exerted on the needle 92 and seal 96 by the bias spring 98, moving the seal 96 and needle away from the seat 106 to allow fluid to escape axially through the pressure relief fluid flow path 80.
  • the actuator guide 58 surrounds the actuator piston 60 and functions to guide the piston in its axial movement relative to the rest of the actuator body 51.
  • the guide 58 also includes a circumferential groove 68 carrying an O-ring type seal 61 which is compressed between the guide 58 and bore 63 communicating with the actuator cavity 26.
  • the guide 58 is received in the bore 63 and axially reciprocates in response to the opposing forces Fi from the wax filled actuator and F 2 from the actuator bias spring 62.
  • the guide 58 is received in the bore 63 communicating with the cavity and reciprocates in sealed relationship with this bore 63.
  • the piston 60 is also received in a smaller diameter bore 65 communicating with the larger bore 63 which receives the guide 58.
  • the bores 63, 65 and relationships between the piston 60, guide 58 and valve body 12 align and control axial movement of the actuator body 51 with respect to the valve housing 12.
  • the piston 60 is manufactured from stainless steel and the guide 58, cup 53 and plunger 64 are constructed of brass.
  • the seal 61 carried by the guide 58 prevents fluid from penetrating behind the guide and entering between the piston 60 and the guide 58. Such penetration can cause corrosion over time, which is prevented by the sealed relationship between the guide 58 and the valve housing 12.
  • freeze protection valve has been set forth for purposes of illustration, the foregoing description should not be deemed a limitation of the invention herein. Accordingly, various modifications, adaptations and alternatives may occur to one skilled in the art without departing from the spirit and the scope of the present invention.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Temperature-Responsive Valves (AREA)

Abstract

L'invention concerne une vanne actionnée thermiquement employant une configuration de vanne avec poussoir et alésage. Un actionneur à cire se dilatant à la chaleur présente une longueur axiale qui varie en réaction à la température régnant dans une cavité de la vanne. À des températures supérieures à un point de réglage prédéterminé, l'actionneur produit un effort axial suffisant pour agrandir la longueur de l'actionneur contre une sollicitation de rappel et faire dépasser le poussoir et le joint dans l'alésage, fermant la vanne. Le poussoir définit un passage d'écoulement de décharge de fluide de la cavité de la vanne à la sortie de la vanne. Une soupape de décharge est disposée dans le poussoir et réagit à la pression régnant dans la vanne. La soupape de décharge s'ouvre pour relâcher la pression au-dessus d'un niveau prédéterminé. La vanne actionnée thermiquement et la soupape de décharge sont coaxiales et emploient une sortie commune.
PCT/US2010/032231 2010-04-23 2010-04-23 Protection antigel intégrée et soupape de décharge WO2011133166A1 (fr)

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PCT/US2010/032231 WO2011133166A1 (fr) 2010-04-23 2010-04-23 Protection antigel intégrée et soupape de décharge

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013153421A1 (fr) * 2012-04-14 2013-10-17 Fricaeco America Sapi De Cv Mécanisme contre la congélation du réchauffeur solaire
CN104685984A (zh) * 2012-09-28 2015-06-03 惠普发展公司，有限责任合伙企业 冷却组件
US9482357B2 (en) 2013-05-29 2016-11-01 Baker Products Ltd. Temperature controlled purge valve for use in water systems
US9529395B2 (en) 2012-03-12 2016-12-27 Hewlett Packard Enterprise Development Lp Liquid temperature control cooling
US10123464B2 (en) 2012-02-09 2018-11-06 Hewlett Packard Enterprise Development Lp Heat dissipating system
US10330395B2 (en) 2013-01-31 2019-06-25 Hewlett Packard Enterprise Development Lp Liquid cooling
US10823304B2 (en) 2016-06-17 2020-11-03 Triteck Limited Freeze prevention valve

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4978060A (en) * 1990-03-15 1990-12-18 Eaton Corporation Engine coolant thermostat with pressure relief feature
US20100032594A1 (en) * 2008-08-07 2010-02-11 Rostra Vernatherm LLC Freeze protection valve

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4978060A (en) * 1990-03-15 1990-12-18 Eaton Corporation Engine coolant thermostat with pressure relief feature
US20100032594A1 (en) * 2008-08-07 2010-02-11 Rostra Vernatherm LLC Freeze protection valve

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10123464B2 (en) 2012-02-09 2018-11-06 Hewlett Packard Enterprise Development Lp Heat dissipating system
US9529395B2 (en) 2012-03-12 2016-12-27 Hewlett Packard Enterprise Development Lp Liquid temperature control cooling
WO2013153421A1 (fr) * 2012-04-14 2013-10-17 Fricaeco America Sapi De Cv Mécanisme contre la congélation du réchauffeur solaire
CN104685984A (zh) * 2012-09-28 2015-06-03 惠普发展公司，有限责任合伙企业 冷却组件
EP2901828A4 (fr) * 2012-09-28 2016-06-01 Hewlett Packard Development Co Ensemble de refroidissement
US9927187B2 (en) 2012-09-28 2018-03-27 Hewlett Packard Enterprise Development Lp Cooling assembly
US10571206B2 (en) 2012-09-28 2020-02-25 Hewlett Packard Enterprise Development Lp Cooling assembly
US10330395B2 (en) 2013-01-31 2019-06-25 Hewlett Packard Enterprise Development Lp Liquid cooling
US10458724B2 (en) 2013-01-31 2019-10-29 Hewlett Packard Enterprise Development Lp Liquid cooling
US9482357B2 (en) 2013-05-29 2016-11-01 Baker Products Ltd. Temperature controlled purge valve for use in water systems
US10823304B2 (en) 2016-06-17 2020-11-03 Triteck Limited Freeze prevention valve

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