US20080127664A1 - Thermostatic expansion valve for refrigeration or heat-pump circuits with thermally controlled safely function - Google Patents

Thermostatic expansion valve for refrigeration or heat-pump circuits with thermally controlled safely function Download PDF

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Publication number
US20080127664A1
US20080127664A1 US11/998,732 US99873207A US2008127664A1 US 20080127664 A1 US20080127664 A1 US 20080127664A1 US 99873207 A US99873207 A US 99873207A US 2008127664 A1 US2008127664 A1 US 2008127664A1
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Prior art keywords
actuating element
valve
temperature
pressure
valve according
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Abandoned
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US11/998,732
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English (en)
Inventor
Joan Aguilar
Rainer Maurer
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Otto Egelhof GmbH and Co KG
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Otto Egelhof GmbH and Co KG
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Assigned to OTTO EGELHOF GMBH & CO. KG reassignment OTTO EGELHOF GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AGUILAR, JOAN, MAURER, RAINER
Publication of US20080127664A1 publication Critical patent/US20080127664A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/36—Expansion valves with the valve member being actuated by bimetal elements or shape-memory elements influenced by fluids, e.g. by the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/063—Feed forward expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the invention relates to a thermostatic expansion valve for a refrigeration or heat-pump circuit as per the preamble of claim 1 .
  • the high-pressure side dissipation of heat takes place usually above the critical pressure of the refrigerant which is used.
  • the pressure at the gas cooler outlet is a degree of freedom in the circuit process.
  • circuit processes which use CO 2 as refrigerant it is highly important to adjust the high pressure into an optimum-efficiency range as a function of the ambient or gas-cooler-outlet temperature.
  • CO 2 air conditioning systems usually only fixed throttles or externally-controlled expansion elements are used in the regulation of the refrigerant circuit. The former do not permit any adaptation of the high pressure to the process boundary conditions during operation.
  • Externally-controlled expansion elements must for this purpose be regulated by electronic control elements whose responsiveness is insufficient in particular for automotive applications. Accordingly, said externally-controlled expansion elements cannot offer a sufficient level of operating reliability. Further disadvantages result from a high susceptibility to failure and high development and purchase costs.
  • DE 102 49 950 B4 discloses an expansion valve for high-pressure refrigeration systems having a valve seat and a valve element which interacts with the valve seat, and a spring device which acts on the valve element, and an adjusting device for the spring arrangement, with the spring arrangement having at least one first spring and one second spring which act on the valve element.
  • the first spring defines a working range and the second spring has a spring force which can be varied by the adjusting device.
  • U.S. Pat. No. 6,012,300 discloses an expansion valve which has a chamber in which refrigerant is enclosed.
  • the chamber is delimited by a diaphragm which acts indirectly on a valve element.
  • the diaphragm is however also exposed to the high-pressure-side refrigerant.
  • the active faces which are acted on by the refrigerant which is enclosed in the chamber and the further active faces which are acted on by the high-pressure-side refrigerant which passes from the gas cooler are identical.
  • no safeguard against high pressure above a maximum permissible value for example 120 bar
  • a reliable start-up behaviour is not possible at inlet temperatures at the expansion valve above the critical temperature of the refrigerant. An operationally reliable application therefore cannot be realized with said expansion valve.
  • DE 10 2005 034 709.6 discloses a thermal expansion valve which has a first and a second active face which are coupled in terms of movement to a valve element.
  • the first active face is part of an expandable separating device which comprises a chamber with a control charge in the thermal head.
  • the temperature of the high-pressure-side refrigerant can be sensed in this way.
  • the temperature-dependent pressure of the control charge in the chamber is transmitted to a temperature-independent spring element which is connected to the second active face which is also subjected to the high pressure.
  • it is intended to obtain a high-pressure limiting function in the supercritical regulating range.
  • a temperature threshold value of the thermally activatable actuating element for an actuating movement is selected which corresponds to a temperature value of the MOT of the control charge.
  • the temperature threshold value is the temperature at which the thermally controllable actuating element generates an actuating or stroke movement.
  • the working characteristic curve of the thermally controlled actuating element has the same gradient as the working characteristic curves of the control charge in the superheated vapour state, but in the opposite direction. The safety function is obtained in this way.
  • an absolute pressure limitation that is to say the realization of the MOP function (maximum operation pressure), is permitted at all temperature levels.
  • the working behaviour of the thermally activatable actuating element is independent of the refrigerant pressure.
  • a detachable mechanical coupling is provided between the first actuating element and the thermally activatable actuating element, and the thermally activatable actuating element engages on a first active face of the first actuating element or on a valve element which is connected to the first actuating element.
  • Said mechanical coupling which occurs above a predetermined temperature value, makes it possible, in normal operation at a conventional temperature threshold range, for the first actuating element to work independently of the thermally activatable actuating element, and the first control element is coupled in terms of movement to the valve element only when a further temperature rise takes place which demands the use of the safety function.
  • the control charge of the first control element is preferably provided in a chamber which is embodied in the manner of a diaphragm or bellows and absorbs the temperature of the high-pressure-side refrigerant.
  • the active face of the first actuating element is acted on by the temperature-dependent pressure of the control charge in the chamber of the actuating element and also by the high pressure.
  • the resulting pressure difference generates an adjusting force which sets the valve element in motion and, as a function of the throttle properties of the associated valve seat, opens a certain flow cross section.
  • an additional, in particular preloaded spring element to be provided which intensifies the action counter to the high pressure.
  • This has the result that an opening movement of the valve element takes place when the temperature-independent excess force, which is generated at the active face by the high pressure of the refrigerant system, is sufficient to overcome the preload of the in particular preloaded spring element and the force action of the chamber, as a result of which a passage between the valve seat and the valve element is opened or the cross section of the passage opening is enlarged.
  • the control charge of the chamber of the first actuating element preferably has a charge density which lies below its critical density. It is preferably additionally provided that a substance mixture is selected for the control charge which has a critical temperature which lies above the critical temperature of the refrigerant to be regulated. In this way, the control charge has, in most temperature threshold ranges, a two-phase state with a high vapour proportion. Only when the energy absorbed by the control charge is sufficient to completely evaporate the liquid phase, which is present as a function of the prevailing filling density, does the control charge pass into the superheated vapour state.
  • a control pressure is generated with only a smaller gradient than in the previous, two-phase state of the control charge, which gradient is not equal to zero.
  • the temperature value above which said physical effect occurs is referred to as MOT (maximum operating temperature).
  • MOP maximum operation pressure.
  • the temperature-independent force of the thermally activatable actuating element corresponds to the increase of the control charge of the first actuating element in the superheated state.
  • the safety function is realized in that the thermally activatable and high-pressure-independent actuating element acts in the opposite direction with the same gradient, so that a maximum operating pressure can be set which, in a desired manner, corresponds to a horizontal pressure profile at a MOP level.
  • Said temperature value or temperature threshold value is preferably determined by the structural design of the thermally activatable actuating element.
  • bimetal elements in particular bimetal plates, which are stacked one on top of the other are provided.
  • Said bimetal plates are for example arranged in the shape of a bellows. Said bimetal elements perform an actuating movement only above a certain temperature, as a function of their pre-setting.
  • a second alternative embodiment for the design of a thermally activatable actuating element provides that a diaphragm, a bellows or a spring element, in particular a spiral spring or a spring bellows, is produced from a shape-memory alloy.
  • a temperature-dependent activation can in turn be made possible in this way.
  • a further alternative embodiment of the actuating element is provided by a filled, bellows-like spring element which is preferably filled with a medium which exists in the liquid state of aggregation above its vaporization pressure or below its saturation temperature.
  • Suitable charge media are for example oil or generally hydrocarbons with a high boiling point.
  • Said temperature displacement transducer elements are preferably hermetically sealingly joined diaphragm, corrugated-tube, bellows elements or else cylinder-piston units which exert high actuating forces by means of thermal expansion of their liquid filling. Said elements can be designed such that their stroke-temperature characteristic curve begins only above a certain temperature.
  • the thermally activatable actuating elements have a pressure-independent device in order to preload them. It is made possible in this way for the temperature value at which the thermal safety function of the valve comes into action to be adjustable.
  • a device of said type is preferably externally adjustable.
  • An electronic or motor-driven activation can alternatively also be provided.
  • the chamber of the first actuating element in particular an inner contour of the chamber, is guided by a sleeve or webs. This makes it possible for deformations as a result of the action of the control charge to be prevented.
  • a minimum passage opening is opened. This means that, when the temperature- and pressure-dependent excess force on the underside of the thermally activatable actuating element is not sufficient to overcome the preload of the latter, only an expediently predefined throttle cross section is opened, and the thermostatic expansion valve functions as a fixed throttle, as a result of which the high pressure in the circuit itself is set.
  • the scope of the present invention therefore encompasses a transcritical or subcritical refrigeration or heat-pump circuit with an inner heat exchanger which makes possible a thermostatic expansion valve with an autonomously settable overflow function or safety function without for example an additional relocation of lines at the evaporation inlet. At the same time, the thermostatic regulating capability of the COP-optimum high pressure can be maintained.
  • FIG. 1 is a schematic illustration of a refrigerant circuit
  • FIG. 2 shows a state diagram for explaining the function of a refrigerant circuit having the thermostatic expansion valve as specified in the introduction
  • FIG. 3 shows a first embodiment of a thermostatic expansion valve
  • FIGS. 4 a,b are a schematic illustration of a control charge characteristic curve and the action of the thermally activatable actuating element on the valve opening characteristic curve
  • FIG. 5 shows a state diagram of valve stroke characteristic curves at different operating pressures
  • FIG. 6 shows a second embodiment of a thermostatic expansion valve
  • FIG. 7 shows a third embodiment of a thermostatic expansion valve.
  • FIG. 1 shows a refrigerant and/or heat-pump circuit 11 of an air-conditioning system.
  • a gaseous refrigerant in particular CO 2
  • the compressed refrigerant is supplied to a gas cooler 13 where a heat exchange takes place between the compressed refrigerant and the environment in order to cool the refrigerant.
  • the refrigerant which leaves the gas cooler 13 passes to an inner heat exchanger 14 which is connected to an expansion valve 15 .
  • the expansion valve 15 has the effect firstly of limiting the pressure of the refrigerant and secondly of regulating the pressure of the refrigerant at the outlet of the inner heat exchanger 14 .
  • the refrigerant passes to an evaporator 16 .
  • the refrigerant absorbs heat from the environment.
  • an accumulator 17 is arranged downstream of the evaporator 16 in order to separate refrigerant of the gaseous phase and of the liquid phase and at the same time to collect liquid CO 2 .
  • the accumulator 17 is in turn connected to the inner heat exchanger 14 .
  • a refrigerant for example CO 2
  • a refrigerant compressor 12 A-B
  • the hot, highly-pressurized, transcritical refrigerant is then cooled in the gas cooler 13 and in the inner heat exchanger 14 (B-C and C-D).
  • the pressure is reduced in the expansion valve 15 (D-E) in order to evaporate the now two-phase (gaseous and liquid phase) refrigerant in the evaporator 16 (E-F), and to thereby extract heat from the environment.
  • the critical temperature of CO 2 lies at approximately 31° C., which is lower than the critical temperature (often >100° C.) of fluorohydrocarbons which have hitherto been used in air-conditioning systems. This has the result that the temperature of CO 2 at the outlet of the inner heat exchanger 14 can be higher than the critical temperature of CO 2 . In said state, the CO 2 itself does not condense at the outlet of the inner heat exchanger 14 . The pressure at the outlet of the inner heat exchanger 14 must therefore be regulated. If, therefore, the external temperature is high, for example in summer, it is necessary to set a high pressure at the outlet of the inner heat exchanger 14 in order to obtain a sufficient cooling power.
  • the outlet temperature at the inner heat exchanger 14 is dependent inter alia on the refrigerant-side temperature at the gas cooler outlet, which is in turn dependent on the ambient temperature. This means that the temperature of the CO 2 at the outlet of the inner heat exchanger 14 can also be used for the regulation of the COP-optimized high pressure, which is otherwise dependent on the refrigerant-side gas cooler outlet temperature.
  • the characteristic curves 21 ′ and 21 ′′ illustrate the COP-optimized regulating region.
  • the double arrow in between denotes a valve stroke range of 0 to approximately 75% of the valve stroke.
  • Illustrated between the characteristic curve 21 ′′ and the characteristic curve 21 ′′′ is the overpressure regulating region.
  • the characteristic curve 21 ′′′′ represents a settable high-pressure limit for the refrigerant circuit 11 which is to be regulated. Said high-pressure limit can be designed to be variable.
  • FIG. 3 illustrates a first embodiment according to the invention of a thermostatic expansion valve 15 which permits operation of a refrigerant system as per a state diagram in FIG. 2 .
  • the expansion valve 15 comprises a valve housing 26 which has a high-pressure side supply opening 27 which leads into a high-pressure space 28 .
  • the high-pressure space 28 is connected by means of a passage opening 29 to a low-pressure side discharge opening 31 .
  • the passage opening 29 has a valve seat 32 in which a valve element 33 is provided in a closed position and separates the supply opening 27 with respect to the discharge opening 31 .
  • a first actuating element 36 which comprises a first active face 37 on which the valve element 33 is provided.
  • a chamber 38 engages on said first active face 37 in the closing direction of the valve element 33 , which chamber 38 is embodied in the manner of a diaphragm or bellows.
  • a spring element 39 which for example surrounds the chamber 38 and preferably engages on the active face 37 in a preloaded manner and in the same force direction as the chamber 38 .
  • a preload of the spring element 39 and/or of the chamber 38 is made possible.
  • the chamber 38 is preferably formed from a highly thermally conductive material.
  • a control charge 41 whose pressure in the chamber 38 is temperature-dependent.
  • a high pressure acts on the high-pressure side, said high pressure acts against the active face 37 and opens the passage opening 29 if the acting high pressure has an excess force with respect to the preloaded spring element 39 and the pressure of the control charge 41 in the chamber 38 .
  • the opening and closing movement is, in the COP-optimized regulating range, independent of a thermally activatable actuating element 46 which is likewise provided in the high-pressure space 28 .
  • the thermally activatable actuating element 46 engages on the first active face 37 opposite the chamber 38 and the spring element 39 , if provided.
  • the actuating element 46 can also engage on the valve element 33 or additionally on the valve element 33 .
  • the thermally activatable actuating element 46 is formed from bimetal plates which are stacked one on top of the other in the shape of a bellows.
  • the bimetal plates can be preloaded by means of a pressure-independent device (not illustrated in any more detail), so that said bimetal places perform an actuating movement or a stroke movement only once the safety function is required. This is the case if the temperature of the refrigerant rises above the MOT. Accordingly, the preload of the bimetal plates or their material configuration is adapted to a temperature threshold value of said type.
  • the optimum cross section is opened and therefore the optimum high pressure (COP-optimized range) is set as a function of the high-pressure-side outlet temperature of the refrigerant at the inner heat exchanger.
  • FIG. 4 a is a schematic illustration of a characteristic curve 19 of a control charge in a chamber 38 of the first actuating element 36 , in which the pressure is plotted against the temperature up to the critical point. Since the control charge, which is present in two-phase form up to said point, passes into the single-phase, superheated gaseous state above the MOT value 20 for the circuit 11 , the pressure of the control charge continues to rise with only a considerably shallower gradient.
  • the safety function can however only be obtained by means of a horizontal pressure profile from the MOT value 20 .
  • Said further disadvantageous rise is compensated in one expedient embodiment of the present invention by means of the use of the thermally activatable actuating element 46 , whose characteristic curve is illustrated with 46 ′ in FIG. 4 a .
  • a valve opening characteristic curve 22 is obtained which is illustrated in FIG. 4 b .
  • Said valve opening characteristic curve 22 with the horizontal pressure profile at the MOP level leads to a maximum mass flow generation when the high pressure of the circuit 11 is situated thereabove, so as to result in a self-inhibiting generation of high pressure, because the temperature-induced pressure force of the chamber 38 , which acts in the closing direction of the valve element 33 , is compensated.
  • the thermally activatable actuating element 46 can also act early on the opening cross section of the passage opening 29 , so that a rise of the high pressure above the MOP value is prevented.
  • the refrigerant-side gas cooler outlet temperature is the preferred regulating temperature in the circuit with regard to COP optimization
  • the high-pressure-side outlet temperature at the inner heat exchanger 14 can likewise be used for the purpose of regulating the high pressure in a COP-optimum range.
  • the outlet states at the inner heat exchanger 14 which correspond to each COP-optimum gas cooler outlet state are determined either by means of simulation or testing for the circuit in which the thermostatic expansion valve 15 described by this invention is used.
  • a COP-optimized pressure profile therefore results by means of the high-pressure-side outlet temperature at the inner heat exchanger 14 , and said COP-optimized pressure profile is the aim of the optimum valve stroke characteristic curve 22 as per the state diagram in FIG.
  • Said COP-optimum valve stroke characteristic curve 22 is restricted to one part, which is to be defined within the context of the application, of the entire valve stroke range, for example between 0 and 75%. This is illustrated in FIG. 2 by the characteristic curves 21 ′ and 21 ′′.
  • the double arrow 22 shows the COP-optimized regulating range. Beyond the upper limit of the latter, the overflow function comes into action.
  • a mass flow rate characteristic curve 23 of the throttle point is designed, above said upper limit, that is to say until 100% of the total valve stroke range is reached, so as to be sufficiently steep that such a mass flow rate can flow out from the high-pressure into the low-pressure side, and therefore a further rise in the high pressure of the system can be prevented, one obtains the safety function, as claimed by the present invention, for preventing excessively high system pressures.
  • thermostatic expansion valve 15 of said type By means of the arrangement of a thermostatic expansion valve 15 of said type at the evaporator inlet, one avoids complex line set relocation, as is necessary for example in the use of a thermostatic expansion valve as per the patent U.S. Pat. No. 6,012,300, since the valve described therein must absorb the refrigerant-side outlet temperature at the gas cooler—either by means of a local arrangement at the gas cooler outlet or by means of the relocation of a capillary line between the valve and gas cooler outlet.
  • FIG. 6 illustrates an alternative embodiment to FIG. 3 .
  • the thermally activatable actuating element 46 is produced as a spring element from a shape-memory alloy. Said actuating element 46 can be set in such a way that the stroke movement takes place only above a predetermined temperature threshold value.
  • the acting force can additionally also be determined by means of the cross section of the spring element.
  • an electric activation of said thermally activatable actuating element 46 composed of the shape-memory alloy could also be possible.
  • the further functions and variants described with regard to FIG. 3 likewise apply to this embodiment.
  • FIG. 7 illustrates a further alternative embodiment of a thermally activatable actuating element 46 to FIG. 3 .
  • a hydraulically filled, bellows-like spring element is provided which permits the overflow function or safety function.
  • the charges of the thermally activatable actuating element 36 comprise for example different oils and hydrocarbons.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Temperature-Responsive Valves (AREA)
  • Sorption Type Refrigeration Machines (AREA)
US11/998,732 2006-12-01 2007-11-30 Thermostatic expansion valve for refrigeration or heat-pump circuits with thermally controlled safely function Abandoned US20080127664A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006057131A DE102006057131B3 (de) 2006-12-01 2006-12-01 Thermostatisches Expansionsventil für Kälte- beziehungsweise Wärmepumpenkreisläufe mit thermisch gesteuerter Sicherheitsfunktion
DE102006057131.2 2006-12-01

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US20080127664A1 true US20080127664A1 (en) 2008-06-05

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US11/998,732 Abandoned US20080127664A1 (en) 2006-12-01 2007-11-30 Thermostatic expansion valve for refrigeration or heat-pump circuits with thermally controlled safely function

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US (1) US20080127664A1 (de)
JP (1) JP2008139013A (de)
CN (1) CN101245961A (de)
CZ (1) CZ2007830A3 (de)
DE (1) DE102006057131B3 (de)
IT (1) ITGE20070115A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070295016A1 (en) * 2006-05-05 2007-12-27 Jean-Jacques Robin Method for controlling an expansion valve and expansion valve, in particular for vehicle air-conditioning systems operated with CO2 as the refrigerant
US10302342B2 (en) 2013-03-14 2019-05-28 Rolls-Royce Corporation Charge control system for trans-critical vapor cycle systems
US10816246B2 (en) 2018-07-30 2020-10-27 Hyundai Motor Company Expansion valve using shape memory alloy spring and air conditioner system for vehicle using the same

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012021746A (ja) * 2010-07-16 2012-02-02 Fuji Electric Co Ltd 電子膨張弁
JP6306827B2 (ja) * 2013-05-16 2018-04-04 アズビル株式会社 回転角度検出器
KR102102958B1 (ko) * 2018-10-11 2020-04-21 한국과학기술원 열팽창 밸브, 그리고 이를 포함하는 저온 냉각 시스템
CN112648761A (zh) * 2020-12-21 2021-04-13 上海交通大学 基于记忆合金的节流控制元件

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Publication number Priority date Publication date Assignee Title
US4015776A (en) * 1976-01-23 1977-04-05 The Singer Company Thermostatic expansion valve
US4347976A (en) * 1977-11-03 1982-09-07 Danfoss A/S Regulating circuit for the valve of a refrigeration plant
US4375753A (en) * 1979-04-02 1983-03-08 Matsushita Electric Industrial Co., Ltd. Air conditioner

Family Cites Families (3)

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Publication number Priority date Publication date Assignee Title
EP0892226B1 (de) * 1997-07-18 2005-09-14 Denso Corporation Drucksteuerventil für Kälteanlage
DE10249950B4 (de) * 2002-10-26 2004-08-12 Danfoss A/S Expansionsventil für Hochdruck-Kälteanlagen
DE102005034709B4 (de) * 2005-07-26 2008-02-21 Daimler Ag Thermostatisches Expansionsventil

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4015776A (en) * 1976-01-23 1977-04-05 The Singer Company Thermostatic expansion valve
US4347976A (en) * 1977-11-03 1982-09-07 Danfoss A/S Regulating circuit for the valve of a refrigeration plant
US4375753A (en) * 1979-04-02 1983-03-08 Matsushita Electric Industrial Co., Ltd. Air conditioner

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070295016A1 (en) * 2006-05-05 2007-12-27 Jean-Jacques Robin Method for controlling an expansion valve and expansion valve, in particular for vehicle air-conditioning systems operated with CO2 as the refrigerant
US10302342B2 (en) 2013-03-14 2019-05-28 Rolls-Royce Corporation Charge control system for trans-critical vapor cycle systems
US10816246B2 (en) 2018-07-30 2020-10-27 Hyundai Motor Company Expansion valve using shape memory alloy spring and air conditioner system for vehicle using the same

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CZ2007830A3 (cs) 2008-06-11
DE102006057131B3 (de) 2007-12-27
ITGE20070115A1 (it) 2008-06-02
CN101245961A (zh) 2008-08-20
JP2008139013A (ja) 2008-06-19

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