WO2005080889A1 - Module d'expansion pour refrigerants - Google Patents

Module d'expansion pour refrigerants Download PDF

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Publication number
WO2005080889A1
WO2005080889A1 PCT/EP2005/050622 EP2005050622W WO2005080889A1 WO 2005080889 A1 WO2005080889 A1 WO 2005080889A1 EP 2005050622 W EP2005050622 W EP 2005050622W WO 2005080889 A1 WO2005080889 A1 WO 2005080889A1
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WO
WIPO (PCT)
Prior art keywords
valve
expansion module
expansion
module according
throttle
Prior art date
Application number
PCT/EP2005/050622
Other languages
German (de)
English (en)
Inventor
Peter Satzger
Gregory Rewers
Original Assignee
Robert Bosch Gmbh
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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2005080889A1 publication Critical patent/WO2005080889A1/fr

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Classifications

    • 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
    • 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

Definitions

  • the present invention relates to an expansion module for a refrigerant of a refrigeration or air conditioning system, in particular for an air conditioning system of a motor vehicle. Furthermore, the present invention relates to such a refrigeration or air conditioning system.
  • the standard version of a refrigeration or air conditioning system essentially consists of an evaporator, condenser (or gas cooler), expansion device, compressor and, if necessary, an internal heat exchanger.
  • a collector is usually part of the standard version.
  • a refrigerant is first compressed by a compressor, the so-called air conditioning compressor, in order to increase the internal energy of the refrigerant.
  • the compressed refrigerant is then cooled in a condenser or condenser by heat exchange.
  • the refrigerant liquefies due to the heat emission associated with the heat exchange.
  • the liquefied refrigerant is then passed through a throttle point of the air conditioning system, this throttle point having an expansion element.
  • the refrigerant passes through the expansion member, the refrigerant expands.
  • the expansion device is usually followed by an evaporator, which is operated as a heat exchanger in order to transfer the released cold to another medium.
  • This other medium can be, for example, air, which depending on the application can then also be supplied to a vehicle heating or cooling system.
  • the condenser is then referred to as a gas cooler, since no condensation occurs in the actual sense, but only a cooling of the supercritical gas is brought about.
  • critically operated compressor refrigeration machines that a refrigerant such as carbon dioxide can be used with a lower compression ratio.
  • Air conditioning systems for motor vehicles in which the refrigerant CO 2 is used, are operated transcritically, that is, depending on the operating conditions, both supercritically and subcritically.
  • the pressure on the high pressure side of the thermodynamic cycle can be controlled or regulated so that the specific cooling capacity of the air conditioning system can be varied. It is thus possible to obtain a maximum effective coefficient of performance by adjusting the pressure on the high-pressure side of the thermodynamic refrigerant circuit as a function of the temperature at the condenser or gas cooler outlet or the ambient temperature.
  • the expansion valve In order to set the high pressure as desired, the expansion valve must make it possible to adjust the flow area depending on the operating conditions, e.g. outside temperature, temperature in the evaporator and depending on the operating strategy, i.e. Optimizing the efficiency or cooling capacity.
  • the operating conditions e.g. outside temperature, temperature in the evaporator and depending on the operating strategy, i.e. Optimizing the efficiency or cooling capacity.
  • the control task of the expansion valve is therefore to adjust the opening cross-section of the valve according to the high pressure.
  • Expansion valves are mainly designed as valves with a ball seat and electromagnetic drive. These valves have the disadvantage of sometimes extreme noise in certain operating conditions. Especially with small volume flows of the refrigerant and thus when the valve is almost closed, the valve ball may hit the valve seat and thus lead to a clear noise development.Therefore, regulation of the pressure with ball seat type valves is problematic, since the previously described noise development e.g. is not acceptable for a vehicle air conditioning system of a motor vehicle.
  • valves have the disadvantage of requiring activation or regulation, which leads to significant additional costs.
  • an expansion valve for a refrigerant of an air conditioning system is known, which is operated electromagnetically and which is essentially a modified pressure control valve for controlling the inlet to the high pressure pump of a fuel injection system of a motor vehicle.
  • DE 101 25 789 C1 discloses a valve arrangement with an expansion valve, to which the refrigerant flows on a high-pressure side and from which the refrigerant emerges again on the low-pressure side.
  • the flow from the high pressure side to the low pressure side is regulated by a throttle body, which works together with a valve seat fixed to the housing and is axially displaceable by an adjusting device.
  • the expansion valve of DE 101 25 789 Cl with its actuating unit is complex and very complex to assemble.
  • the object on which the invention is based is to present an expansion module which ensures good control characteristics and, moreover, at the same time an inexpensive construction.
  • the expansion module according to the invention for a refrigerant which is used in particular for the controlled expansion of a refrigerant or air conditioning system on the high pressure side to a low pressure level, has an expansion valve which is in the form of a rail Ownership valve is formed, wherein the sliding seat serving as a valve piston is controlled by at least one pressure applied to the valve.
  • the expansion module according to the invention By designing the expansion module according to the invention with a pressure-controlled sliding seat valve, it is possible in an advantageous manner to implement an expansion module which enables both good controllability and simple and therefore inexpensive implementation. In particular, electrical control of the expansion module with appropriate lines, plug elements and at least one control unit is not required. Since the expansion module according to the invention is only pressure-controlled, regulation of the refrigerant circuit and in particular the expansion of the refrigerant can be implemented using simple mechanical means.
  • the use of the expansion module according to the invention in an air-conditioning or refrigeration system advantageously enables the thermal efficiency of the air-conditioning system to be improved without complex control being necessary.
  • the characteristic of the throttle cross section of the expansion module can be set as a function of, for example, the high pressure level or the pressure difference across the valve.
  • the valve piston of the expansion valve of the expansion module according to the invention is controlled by at least one pressure of the refrigerant applied to the valve. Electromagnetic control of the throttle body is not necessary.
  • valve piston of the expansion valve designed as a sliding seat valve, which is axially displaceable in a valve chamber of the valve housing, is adjusted against the force of a spring-elastic element.
  • the force applied by the resilient element to the displaceable valve piston is advantageously adjustable.
  • the pre-tensioning of the spring-elastic element can be done with a countermeasure, such as a screw or a disc dance disc are already adjusted during production, so that a desired valve characteristic of the expansion valve of the expansion module according to the invention results.
  • the spring preload can also be set by an actuator, a magnet or thermostatically. In this way it is then possible to set both the high pressure level and the low pressure level in a refrigeration cycle. In particular, it is advantageously possible to adapt the core line during operation of the system.
  • the expansion module according to the invention has a valve piston which is designed as a throttle body and which has at least one throttle opening which can be overlapped with a corresponding opening in the valve housing of the expansion valve.
  • the opening in the valve housing is also referred to as "throttle opening", although there is no throttling here. This designation is only used to assign this opening of the valve housing to the throttle opening in the throttle body of the valve and to delimit this opening in the valve by By moving the valve piston or the throttle body relative to the housing of the expansion valve and thus to the so-called throttle opening, which is formed in the housing of the expansion valve, a more or less large expansion area can be released for the refrigerant.
  • the at least one throttle opening of the throttle body of the expansion valve is positioned in the valve piston such that the valve is closed in the depressurized state.
  • the expansion module according to the invention can have an expansion valve with a throttle opening of the throttle body, which has a total opening area in the range from 0.5 to 10 mm 2 , in particular from 1 to 7 mm 2 .
  • the throttle opening of the throttle body is essentially slot-shaped and extends in the axial direction on the cylinder jacket of the valve piston of the valve.
  • the valve characteristic curve can also be adjusted using the specially selected slot geometry.
  • the valve housing has In an advantageous embodiment of the expansion module according to the invention, in addition to the opening referred to as the throttle opening, at least one further inlet channel and at least one further outlet channel.
  • the valve piston of the expansion valve can be controlled by the pressure difference between the inlet channel and the outlet channel of the valve.
  • a defined position of the throttle body in the valve housing is established via an equilibrium of forces on the valve piston, ie on the throttle body, which is established between the pressure forces and the force of the spring-elastic element.
  • Expansion valve changes.
  • any characteristic of the throttle cross section can be in
  • the expansion valve has on its low-pressure side an active body, or a disk, which is in operative connection with the valve piston of the expansion valve.
  • This active body is connected to the valve housing via a membrane or a bellows in such a way that two separate subspaces are created on the low-pressure side of the valve.
  • the low pressure prevails on one surface side of the active body and an ambient pressure of the valve on its opposite surface side.
  • the membrane or the bellows can also be replaced by a gas cushion or an elastic body, such as a rubber spring.
  • valve piston of the expansion valve it is possible for the valve piston of the expansion valve to be controllable by the pressure difference between the high pressure level and the ambient pressure of the valve.
  • the force resulting from the low pressure has to be compensated in the force balance above the valve piston. This is possible because of the knitted body in connection with the membrane or the bellows low pressure on one side and ambient pressure on the other side. If one connects the mostly rigid active body with the valve piston serving as a throttle body, the resulting compressive force on the active body can also act on the piston. A position of the throttle body via the high pressure or the differential pressure between the high pressure side and the ambient pressure of the refrigeration circuit is thus advantageously possible.
  • the expansion module according to the invention has, in addition to the expansion valve, a fixed throttle with a constant throttle cross section.
  • the opening cross section of the constant throttle is then independent of the high pressure prevailing in the circuit.
  • the pressure-controlled expansion valve described is operated parallel to the constant throttle.
  • the expansion module according to the invention which on the one hand has a fixed throttle with a constant throttle cross-section and on the other hand has a pressure-driven expansion valve, enables a good control characteristic with a cost-effective design.
  • the expansion module according to the invention can be used to implement an air conditioning system, in particular an air conditioning system for a motor vehicle, which, depending on the operating conditions, for example outside temperature, temperature in the evaporator or also operating strategy, i.e. For example, optimization of the efficiency or optimization of the cooling capacity is adjustable.
  • FIG. 1 shows a schematic illustration of an embodiment of a refrigerant circuit according to the invention
  • FIG. 2 shows a first exemplary embodiment of a pressure-controlled expansion valve of the expansion module according to the invention in a schematic basic illustration
  • FIG. 4 shows another example of a pressure-controlled expansion valve of the expansion module according to the invention
  • Figure 5 shows another example of a pressure-controlled expansion valve
  • FIG. 6 shows a first embodiment for a valve piston of an expansion valve of the expansion module according to the invention, which valve serves as a throttle body
  • FIG. 7 shows a graphical representation of the functional relationship between the pressure at the inlet of the valve and the opening cross section of the expansion valve for different sizes of the throttle opening
  • FIG. 8 shows an alternative embodiment of a throttle body for an expansion valve
  • FIG. 9 shows the functional dependency belonging to FIG. 8 between the pressure at the inlet of the valve and the opening cross section for different sizes of the throttle opening of the throttle body.
  • the air conditioning or refrigeration system 12 shown in principle in FIG. 1 comprises a compressor 50, a condenser or gas cooler 52, an expansion module 10 and an evaporator 54, which are connected to one another via corresponding connecting means 56 and form a refrigerant circuit.
  • the components of this circuit are operated in the manner of a compression refrigeration circuit.
  • the refrigerant for example the refrigerant CO2
  • the compressor the so-called air conditioning compressor 50
  • the compressed refrigerant is then cooled in a condenser or condenser 52 by heat exchange.
  • the refrigerant in the condenser is not liquefied, but only cooled as a gas in the supercritical state.
  • this heat exchanger is also referred to as a gas cooler when the supercritical mode of operation of the refrigerant is used.
  • the refrigerant cooled in this way is then expanded to a lower pressure by means of an expansion module 10 and is further cooled in the process.
  • the expansion module 10 is generally followed by an evaporator 54, which is operated as a heat exchanger in order to transfer the released cold of the refrigerant to another medium.
  • This other medium which interacts with the cold, expanded refrigerant via the evaporator 54, can be, for example, air which is fed to a heating or cooling system (air conditioning system) of a motor vehicle.
  • a heating or cooling system air conditioning system
  • the pressure on the high pressure side of the thermodynamic cycle can be controlled or regulated.
  • the specific cooling capacity of the air conditioning system can be varied as desired. It is thus possible to obtain a maximum effective coefficient of performance by adjusting the pressure on the high-pressure side of the thermodynamic cycle (high-pressure level) as a function of the temperature at the gas cooler outlet or the ambient temperature.
  • the high pressure level can be set independently of the temperature when the heat is emitted.
  • control and / or regulatable expansion devices can be used.
  • the expansion module 10 therefore has at least one controllable expansion valve 14.
  • a fixed throttle (orifice) 70 with a constant throttle cross section can also be used.
  • the controllable expansion valve 14 and the orifice 70 are then arranged parallel to one another in an expansion module 10 and, as shown in the schematic illustration in FIG. 1, integrated in the refrigerant circuit 12.
  • FIG. 2 shows a first exemplary embodiment of a pressure-controlled expansion valve for the expansion module according to the invention.
  • the expansion valve 14 according to the invention has a valve housing 28 in which a valve chamber 26 is provided.
  • a valve piston 22 is axial, i.e. arranged displaceably in the direction of the axis 58.
  • the valve piston 22 and or the piston guide 32 in the exemplary embodiment according to FIG. 2 are coated with low friction, for example with a Teflon or carbon coating.
  • the valve piston 22 of the expansion valve according to the embodiment of FIG. 2 is adjustable against the force of a spring-elastic element 38, which is shown schematically as a spring in FIG. 2.
  • the valve according to the invention according to FIG. 2 has two inlet openings 60 and 62 in its valve housing, which are connected to the high-pressure side HD of the refrigerant circuit according to FIG. 1 in the installed state of the expansion valve. An outlet opening 64 is then connected to the low-pressure side ND of the refrigerant circuit.
  • the high pressure HD is applied to the radial inlet channel 62 of the valve housing 28.
  • This inlet channel 62 opens into an opening 30 of the valve housing 28, which is referred to below as the throttle opening of the valve housing, although no throttling takes place here.
  • This designation only serves to assign this opening of the valve housing to the throttle opening in the throttle body of the valve and to differentiate this opening 30 in the valve from further valve openings or inlet or outlet channels.
  • the throttle opening 30 of the valve housing 28 can, depending on the position of the Ventilgro ⁇ ers 22, with a throttle opening 20, which is formed in the cylinder of the valve piston 22, overlap more or less.
  • the valve piston 22 is thus designed as a throttle body 18 which has at least one throttle opening 20 which can be brought into operative connection with the throttle opening 30 of the valve housing 28, so that a continuous connecting channel is established between the high pressure side of the valve and the low pressure side of the valve.
  • a defined position of the valve piston 22 in the valve housing 28 is established via a balance of forces between the pressure forces acting on the valve piston 22 and the spring force of the spring-elastic element 38.
  • a change in the pressure force shifts the valve piston 22 in its position.
  • a change in position of the valve piston 22 leads to a change in the overlap between the throttle opening 30 in the valve housing and the throttle opening 20 of the valve piston 22 serving as throttle body 18. In this way, the throttle cross section of the expansion valve is changed.
  • any desired Kerm line of the throttle cross section can be set depending on the pressure difference across the valve.
  • valve piston 22 Through various configurations and arrangements of elastic spring element 38, valve piston 22 and inlet openings 60, 62 for the refrigerant at high pressure can the desired characteristic of the throttle cross section of the expansion valve according to the invention can be set as a function of the I3mck difference above the valve.
  • the expansion valve 14 according to the invention can also be flowed through in the opposite direction , as indicated by the arrows 70 in Figures 2 and 3.
  • the expansion valve according to the invention is controlled via the high-pressure level of the refrigerant circuit.
  • the force resulting from the low pressure must be compensated in the force balance acting on the valve piston. This is possible, for example, through an additional active body which is integrated into the valve according to the invention.
  • FIG. 4 shows such an exemplary embodiment for an expansion valve of the expansion module according to the invention.
  • the active body 40 is arranged inside the valve housing 28 on the low pressure side of the valve and separates the low pressure level ND from the ambient pressure UD with the aid of the membrane 50. This can be done, for example, by dividing the space 48 below the valve piston 22.
  • On one surface side 42 (in the 4 corresponds to the upper surface of the active body 40 or the membrane 50 facing the valve piston 22), the low pressure ND of the refrigerant circuit acts.
  • the opposite surface side 44 which corresponds to the lower surface of the knitted body or the membrane facing away from the valve piston 22 in the exemplary embodiment in FIG. 4) of the knitted body, the ambient pressure of the valve prevails.
  • Screw 72 are indicated. If this screw is screwed further into the valve housing 28, the preload of the spring-elastic element increases.
  • Other options for setting the force exerted by the resilient element on the active body or on the valve piston are of course also possible, the screw serves in this only the symbolic representation of possible setting means.
  • a servomotor, a magnet or a thermostatic actuating element should also be mentioned here, which ensure the adaptation of the characteristic curves of the valve even during operation of the system.
  • the expansion valve according to the invention can also be flowed through in reverse.
  • the specification of a special contour and size of the throttle opening 20 in the throttle body 18 of the valve according to the invention enables the generation of a desired characteristic curve for the expansion module.
  • throttle openings 20 are shown in the cylindrical shape of the valve piston 22.
  • the typical throttle cross-sectional area should be in a range of approximately 0.5 to 10 mm 2, in particular in the range of 1 to 7 mm 2 .
  • FIG. 6 shows the example of a throttle opening stepped in the axial direction of the valve
  • the throttle opening according to FIG. 8 has a trapezoidal contour.
  • Other contours for the throttle openings 20 are of course also possible.
  • the contour of the at least one throttle opening can expand more or less both concavely and convexly or discontinuously in the axial direction compared to a trapezoidal expansion, as shown in FIG.
  • the characteristic curve of the valve can be adjusted using various slot geometries. The geometries shown here are only examples and not subsequently.
  • valve 14 Due to the axial, pressure-driven movement of the valve piston 22 in the valve guide 32, depending on the position of the valve piston 22 relative to the throttle opening 30 of the valve housing 28, only part of the throttle opening or throttle openings 30 and thus the flow Throttle performance of the expansion valve varies.
  • the valve 14 according to the invention is either completely open or closed at a predetermined pressure level.
  • the pressure difference across the throttle opening 20 increases with a reduction in the throttle cross section.
  • the pressure at the inlet of the expansion valve 14, i.e. the high pressure HD of the refrigeration system can be set specifically.
  • the high pressure of the refrigeration system can be set to desired values by adapting the contour of the throttle opening 20 or the strength of the spring-elastic element 38.
  • the ratio of the axial travel of the valve piston 22 to the opening of the throttle cross section and thus the valve characteristics of the expansion module according to the invention can be varied by means of different contours of the throttle openings, as are shown, for example, in FIG. 6 or FIG. 8.
  • the characteristic curve of the valve can thus be adapted via various slot geometries.
  • FIG. 7 (corresponding to the embodiment of a throttle body according to FIG. 6) and FIG. 9
  • FIGS. 7 and 9 each show in a schematic representation the valve characteristics of the expansion module according to the invention.
  • the corresponding valve pistons 22 with the contours of their throttle openings 20 are again shown in the figures in FIGS. 7 and 9.
  • the abscissa of the graphical representation of FIG. 7 or FIG. 9 corresponds to the stroke of the valve piston 22 or throttle body 18 and is thus a function of the differential pressure applied to the valve.
  • Plotted on the ordinate of the representations in FIGS. 7 and 9 is the flow rate F, which essentially corresponds to the throttle cross section at the respective position of the throttle body 18.
  • the individual curves show the valve characteristics for different total throttle cross sections A, with the arrow shown the
  • Typical throttle cross-sectional areas A are in a range from approx. 0.5 to 7 mm 2 .
  • a fully closed sliding seat valve typically has an internal leakage that depends on the difference in pressure across the valve and the gaps between the valve piston 22 and the valve guide 32.
  • the expansion valve according to the invention has both the gap height and the gap length between the valve piston and the Piston guide modified in such a way that a predeterminable, adequate tightness of the fully closed expansion valve is achieved.
  • valve piston and / or the piston guide low-friction for example with a
  • Teflon or carbon layer to coat Teflon or carbon layer to coat.
  • the expansion module according to the invention has, in addition to the controllable expansion valve, an additional throttle, constant opening, which is arranged parallel to the expansion valve in terms of flow technology.
  • the expansion module according to the invention is not limited to the exemplary embodiments of the expansion valve listed in the description.
  • the expansion module according to the invention is moreover not limited to use in the refrigerant circuit of an air conditioning system shown.
  • the refrigeration or air conditioning system according to the invention is not restricted to the use of CO 2 as refrigerants.
  • the air conditioning system according to the invention is not limited to the use of only one expansion valve. It is advantageously possible for the expansion module to also have a plurality of expansion valves which are connected to one another in terms of flow technology. Furthermore, it is possible in principle to operate the refrigerant circuit according to the invention as a heat pump.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Fluid Mechanics (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention concerne un module d'expansion (10) pour réfrigérants, notamment un module (10) d'expansion contrôlée qui comprend au moins une soupape d'expansion (14) d'un réfrigérant du côté haute-pression d'un système de réfrigération et/ou de climatisation (12) jusqu'à un niveau de basse pression. Selon l'invention, la soupape d'expansion (14) du module d'expansion (10) a la forme d'une soupape (16) à siège coulissant. Le siège coulissant (24), qui sert de piston à soupape (22), est commandé par au moins une pression appliquée à la soupape. L'invention concerne en outre un circuit réfrigérant, notamment un circuit réfrigérant d'un système de climatisation pourvu d'au moins un module d'expansion de ce type.
PCT/EP2005/050622 2004-02-19 2005-02-14 Module d'expansion pour refrigerants WO2005080889A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004008434 2004-02-19
DE102004008434.3 2004-02-19

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007079969A1 (fr) * 2006-01-09 2007-07-19 Thomas Magnete Gmbh Soupape à tiroir longitudinal, en particulier pour l'utilisation de cycles de climatisation transcritiques au co2 (r 744)
WO2009060465A2 (fr) * 2007-07-18 2009-05-14 Vijay Appa Kasar Dispositif d'expansion économiseur d'énergie pour la réfrigération et autres branches d'industrie
DE102009025597A1 (de) * 2009-06-19 2010-12-23 DENSO CORPORATION, Kariya-shi Kältekreis mit einem Expansionsventil und Verfahren zum Betrieb des Kältekreises
CN103954081B (zh) * 2014-04-15 2016-03-30 朱德仲 一种防滑式节流活塞
DE102017107296A1 (de) * 2017-04-05 2018-10-11 Hanon Systems Absperrventil und Fluid-Absperreinrichtung eines Kältemittelverdichters

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WO2007079969A1 (fr) * 2006-01-09 2007-07-19 Thomas Magnete Gmbh Soupape à tiroir longitudinal, en particulier pour l'utilisation de cycles de climatisation transcritiques au co2 (r 744)
WO2009060465A2 (fr) * 2007-07-18 2009-05-14 Vijay Appa Kasar Dispositif d'expansion économiseur d'énergie pour la réfrigération et autres branches d'industrie
WO2009060465A3 (fr) * 2007-07-18 2009-08-27 Vijay Appa Kasar Dispositif d'expansion économiseur d'énergie pour la réfrigération et autres branches d'industrie
DE102009025597A1 (de) * 2009-06-19 2010-12-23 DENSO CORPORATION, Kariya-shi Kältekreis mit einem Expansionsventil und Verfahren zum Betrieb des Kältekreises
CN103954081B (zh) * 2014-04-15 2016-03-30 朱德仲 一种防滑式节流活塞
DE102017107296A1 (de) * 2017-04-05 2018-10-11 Hanon Systems Absperrventil und Fluid-Absperreinrichtung eines Kältemittelverdichters

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