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WO2007079969A1 - Soupape à tiroir longitudinal, en particulier pour l'utilisation de cycles de climatisation transcritiques au co2 (r 744) - Google Patents

Soupape à tiroir longitudinal, en particulier pour l'utilisation de cycles de climatisation transcritiques au co2 (r 744) Download PDF

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Publication number
WO2007079969A1
WO2007079969A1 PCT/EP2006/012557 EP2006012557W WO2007079969A1 WO 2007079969 A1 WO2007079969 A1 WO 2007079969A1 EP 2006012557 W EP2006012557 W EP 2006012557W WO 2007079969 A1 WO2007079969 A1 WO 2007079969A1
Authority
WO
WIPO (PCT)
Prior art keywords
slide
valve according
slide valve
control
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2006/012557
Other languages
German (de)
English (en)
Inventor
Axel MÜLLER
Rene Schulz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Thomas Magnete GmbH
Original Assignee
Thomas Magnete 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 Thomas Magnete GmbH filed Critical Thomas Magnete GmbH
Priority to EP06841182A priority Critical patent/EP1971809A1/fr
Publication of WO2007079969A1 publication Critical patent/WO2007079969A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
    • F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
    • F16K3/26—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members with fluid passages in the valve member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0668—Sliding 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • 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
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F25B41/345—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by solenoids
    • 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
    • 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
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the invention relates to a longitudinal slide valve according to the preamble of claim 1.
  • R 744 is the name for a refrigerant based on CO 2 . Apart from short-term effects, the R 744 refrigerant is environmentally neutral, has a very low ozone depletion potential with respect to the Earth's atmosphere and is characterized by a very low global warming potential.
  • Control valves are designed as flat, rotary and longitudinal slide valves, which have a good control behavior. They are able to cope with high pressures and high volume flows in a small volume and with relatively little effort. The disadvantage, however, that they have high leakage currents due to unavoidable gaps between the spool and the guide cylinder of the valve, which must be dissipated. In order to be able to meet the demand for the least leakage, pure seat valves or combined slide seat valves are often projected in a transcritical R 744 air conditioning cycle, since with pure slide valves, demands for minimal internal leakage seem inaccessible for this application.
  • DE 103 05 947 A1 shows a slide valve as an expansion element for controlling the transcritical range of an air conditioning system with the refrigerant R 744, which is unavoidably characterized by internal leakage.
  • DE 34 46 384 C2 describes a flat slide valve as a switching valve, wherein a fluid flow is switched by means of a tilting pipe between two terminals. The tilting tube is actuated by means of a flat slide.
  • DE 40 27 610 C2 discloses a switching valve with a two-part planar valve slide, in which the two parts are elastomerically sealed from each other. The slider is moved between two sealing surfaces.
  • DE 38 20 525 C2 shows an air distributor with a slide designed as a flat slide, which is mounted laterally to its on-flow direction. The foil is passed with considerable play.
  • DE 43 04 440 B4 shows a valve with two housing parts, which has two openings for the supply and discharge of a fluid.
  • a thin foil slide in the form of a plate is moved transversely to the flow direction of the fluid.
  • the valve gate has through openings for the passage or blocking of the fluid transversely to the direction of flow of the fluid.
  • the foil slide is arranged with an additional spacer in a plane with the slider between the two housing parts.
  • DE 44 16 056 C2 shows a slide valve with a movable in the axial direction flat film slide, which is designed as a thin sheet. Depending on the approached slide position, one or more pressurized inflows and outflows are partially or completely released by switching sections on the flat slide.
  • DE 35 34 460 shows a high-pressure valve with a channel in which a lateral inlet opens and which contains a valve slide which can be displaced axially over the inlet.
  • the slider has an integrally molded tubular portion which presses radially against the wall of the channel. The sealing effect is thereby increased pressure-dependent.
  • the invention has for its object to provide a longitudinal slide valve in almost leak-free design, which compared to the known arrangements has improved control behavior and is also suitable for use in the high pressure range and in particular in trans-critical R 744 air conditioning circuits.
  • the object is achieved in conjunction with the preamble by the characterizing features of claim 1.
  • the slide valve according to the invention combines two positive properties: the avoidance of internal leakage in the closed state of the connection openings and at the same time an improved control behavior due to the largely free configurability of flow-stroke characteristics. This requires no additional seat body.
  • an elastically resilient radially yielding spool By means of an elastically resilient radially yielding spool the connections for one or more inlets or outlets are sealed against each other.
  • the radial force component of the pressure difference between inlet pressure and discharge pressure is used, which presses the thin wall of the tubular slide radially against the wall of the valve sleeve and there arranged pressure-loaded connection openings, without pressure difference remains a gap with fluid, the greater than allowed if the leakage requirements are to be met.
  • the slider or the valve housing has a formable opening contour for the flow of the fluid. This allows almost any adjustment of the flow to the stroke characteristic of the actuator.
  • the tubular design does not require a spacer or a seal between planar foils. In principle, any tube shape can be used, but preferably round tubes or those with rounded cross section.
  • the control slide comprises a thin-walled elastic film.
  • a tubular film slide has in the axial direction the necessary rigidity for the adjustment of the slide in this direction, with simultaneous elastic deformability in the radial direction.
  • both openings must be located directly above one another.
  • an annular groove or a securing element is advantageously provided against a rotation of the slide.
  • Such a rotation can be realized both by means of a guide pin in the housing, or by being combined with a plunger of the actuating element or is designed as part of the slide.
  • the conversion of the slider can consist in an advantageous manner exclusively of the film material.
  • the slider is hollow inside.
  • the flow path from the interior of the slide to the radial opening in the slide and from there to the opening in the valve sleeve When the valve position is open, the flow path from the interior of the slide to the radial opening in the slide and from there to the opening in the valve sleeve.
  • the end faces of the slide for this purpose are advantageously stiffened or have inserted stiffening surfaces with axial passage to the interior of the slider so that the pressure can be there.
  • the stiffeners can either take the entire face as a perforated plate or only a partial area in the form of a ring.
  • the design of the above-described embodiments of the slider, in particular its compliance, and the housing is to be subjected to an optimization.
  • the elastic deformation can advantageously act sealingly over the entire length of the slider or only in sections.
  • the friction between slide and sleeve is reduced by design measures and by a suitable choice of the material pairing slide and housing. Frictional effects can be reduced by slits, grooves, surface roughness or other suitable measures both on the slider circumference and on the surface of the wall.
  • the grooves are designed in such a way that with their help corresponding pressure fields are specifically influenced. With the help of a circumferential groove can be z. B. achieve that even with a rotation of the spool, the desired flow is ensured.
  • the arranged on the slide and / or on the wall of the bore grooves, grooves or channels - or the surface itself - store advantageous lubricants. This reduces frictional effects between the sliding components.
  • the lubricant storage in the grooves has the advantage that the lubricant is not completely displaced in the phase of a high pressure difference prevailing at the ends of the slide.
  • the force effect of the pressure difference for leak-free sealing in the closed state is additionally reinforced by spring force.
  • the slider contains additional elastic elements or a resilient mounting or even forms an elastically resilient spring element.
  • the interpretation of such a spring is also carried out according to the calculations of all the effects of force, u. a. the flow, spring and pressure forces in the valve, so that the radial force effect of the tube sheet at the actual pressures acting on the connections, is exactly sufficient.
  • valve sleeve and a surrounding housing can advantageously be made in one piece, as compared to the flat slide on the storage of the slide between two housing parts and optionally other components, such as spacers, can be dispensed with. This saves additional seals on the valve housing or between individual valve housing parts, thus reducing the risk of potential damage. for leaks drastically reduced.
  • the valve housing in space-saving form in cartridge design (Cartridge) can be performed.
  • a further advantageous embodiment of the invention comprises, in particular, an electromagnet as actuating device for the slide whose armature forms the actuating element for the valve slide with an axially extended rod tappet.
  • an electromagnet as actuating device for the slide whose armature forms the actuating element for the valve slide with an axially extended rod tappet.
  • the current flow of the magnet is proportional to the stroke of the armature and thus the applied force to one of the end faces of the slide. The control behavior of the valve is thus directly influenced by the current supply.
  • the valve is particularly suitable for use in transcritical CO 2 (R 744) air conditioning circuits in mobile applications.
  • the refrigerant is compressed to over 100 bar, while the circuit for conventional refrigerant only passes through a pressure difference of about 30 bar.
  • the high pressure difference in the R 744 refrigerant as fluid causes a strong radial elastic deformation of the slide for controlling and sealing the inflow and outflow in the valve sleeve.
  • the valve sleeve has a pressure-tight enclosure.
  • the inventive valve advantageously controls the adjustment of the compressor or overheating or high pressure level of the refrigerant.
  • the figure shows a longitudinal section of an electromagnetically actuated control valve 1 for use in an air conditioning circuit for an air conditioner, which is based on a transcritical R 744 (CO 2 ) air conditioning cycle.
  • the refrigerant is significantly more ker compressed than is required with conventional refrigerants.
  • This requirement profile requires for the valve 1 on the one hand a pressure-resistant design and on the other hand high demands on values of the external and internal leakage and very good control technical properties.
  • the valve 1 is a direct-acting 2/2-way spool valve which is controlled by the magnetic force of an electromagnetic actuator 2 substantially including the right part of the drawing. Shown is the currentless open type, d. H. Connection openings for a respective inflow or outflow 22 are connected to one another in the illustrated position of the control or valve slide 18 of the valve 1. By magnetic force, the slider 18 is moved axially to the left, the flow path between the inlet and the outlet 22 is then locked.
  • the electromagnet 2 has a pot-like housing 3, whose
  • a lid 4 Bottom of a lid 4 is completed, and in which a cylindrical magnetic body is inserted. On the outer lid surface, a connection 5 for the energization of the magnet 2 is arranged. In this way, a cylindrical coil 6 arranged inside the housing 3 is energized.
  • the magnetic field generated by the energization of the solenoid 6 is closed by a magnetic pole 7 with control cone 8, an armature 9, which consists of armature piston 13 and acting as an actuator 11 anchor rod, and the flux-conducting part of the housing 3 with the yoke 10, wherein the actuating rod 11 in the armature counterpart, the magnetic pole 7, is displaceable in the direction of the open housing 3 and projects to the outside as an actuator or control member for the spool valve 18 of the valve 1 to the left.
  • the armature piston 12 is connected to the actuating rod 11.
  • the piston 12 has for this purpose an axial opening.
  • the front part of the Opening serves to support the hollow actuating rod 11, the rear part is used to equalize the pressure in the interior of the valve 1.
  • the yoke 10 between the cover 4 and cylindrical coil 6 is arranged and designed as a disc.
  • the armature piston 12 is arranged axially movable together with the actuating rod 11 within the range of the control cone 8. By energizing the solenoid 6, both components are moved axially to the left.
  • the magnetic pole 7 has a coaxial recess as a stroke limiter with radial edge webs with a contour falling at the end in the direction of the armature stroke, which forms the control cone 8. Due to the design of the control cone 8, the flow force-stroke characteristic of the electromagnet 2 is influenced so that the applied current is proportional to the stroke of the actuating rod 11 and thus directly affects the setting or control variable of the valve spool 18. On the radially extending surface of the stroke limiter, an adhesive disc 13 is attached from non-magnetic material, which dampens the armature stroke to the left and thus prevents bouncing of parts meeting each other.
  • the armature piston 12 is guided in a thin-walled pressure-resistant sleeve 14, which rests with its closed end outwardly against the cover 4 and inside the armature piston 12, the web of the control cone 8 and most of the outer wall of the magnetic pole 7 surrounds.
  • the pressure-resistant sleeve 14 is joined to the armature counterpart, that the joint itself is pressure-resistant and free of external leakage
  • valve 1 which essentially comprises the left area of the drawing, is formed by a valve sleeve 15 surrounding the valve 1. It forms a structural with the magnetic pole 7 Unit which is inserted in the magnetic body. The result is a compact valve 1 with a small size.
  • valve sleeve 15 On the outer peripheral surface of the valve sleeve 15, a radial bore 16 for an inflow and outflow 22 of the refrigerant R 744 is arranged. The corresponding counterpart is arranged on the stroke of the actuating rod 11 opposite end face of the valve sleeve 15.
  • the valve sleeve 15 has an axial bore 17 extending over its entire length. This extends in the axial direction from the right end of the valve sleeve 15, which includes the corresponding counterpart of the inflow or outflow 22, to the radial stroke limitation of the magnetic pole 7.
  • the radial bore 16 of the drain 22 opens in a circumferential groove in the axial bore 17th
  • valve sleeve 15 has an O-ring seal 21. Another seal 19 seals the valve sleeve 15 from the environment.
  • the spool 18 is arranged, which is designed as a tubular film slide, and the peripheral wall 20 is radially elastically deformable.
  • the two end faces 24a and 24b of the spool 18 each have radial stiffeners 25a and 25b.
  • a compression spring 27 is arranged, which is arranged with its one end against a arranged on the end face of the valve sleeve 15, annular spring receptacle 28 and with its other end against the annular Stiffening 25 a of the spool 18 acts.
  • the spring 27 acts as a restoring element against the force acting on the opposite, right end face 24b magnetic force.
  • the peripheral surface of the slide has, in the amount of the inflow and outflow, a control opening 26 which serves as an opening in the peripheral wall 20 is shown.
  • the two connection openings are connected together in this position.
  • stiffener 25b is designed as a plate with axial openings, which serves as a stop surface for the actuating rod 11 of the armature 9. Through the axial openings in the right stiffener 25b, the space to the right of the stiffener 25b to the right end of the armature piston 12 is also pressurized.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Multiple-Way Valves (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention concerne une soupape à tiroir longitudinal qui comprend un manchon (15) présentant au moins deux ouvertures de raccordement pour l'arrivée et l'évacuation (22) d'un fluide sollicité en pression dans un logement (17) axial à l'intérieur du manchon (15). Un tiroir de commande (18) déplacé par un élément d'actionnement (11) d'un dispositif d'actionnement (2) est disposé dans ledit logement (17), ce tiroir présentant au moins une ouverture de commande radiale (26) par l'intermédiaire de laquelle une fonction de commutation et de réglage est produite pour une voie d'écoulement du fluide en cas de déplacement axial du tiroir (18). Le système selon l'invention se caractérise en ce que le tiroir de commande (18) présente une paroi périphérique tubulaire (20) qui peut être déformée élastiquement dans le sens radial et qui est plaquée contre le logement (17) axial du manchon (15) en cas de sollicitation radiale en pression, l'étanchéité étant assurée entre les ouvertures de raccordement.
PCT/EP2006/012557 2006-01-09 2006-12-27 Soupape à tiroir longitudinal, en particulier pour l'utilisation de cycles de climatisation transcritiques au co2 (r 744) Ceased WO2007079969A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06841182A EP1971809A1 (fr) 2006-01-09 2006-12-27 Soupape à tiroir longitudinal, en particulier pour l'utilisation de cycles de climatisation transcritiques au co2 (r 744)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006001142A DE102006001142B3 (de) 2006-01-09 2006-01-09 Längsschieberventil, insbesondere für die Verwendung von transkritischen CO2 (R 744) Klimakreisläufe
DE102006001142.2 2006-01-09

Publications (1)

Publication Number Publication Date
WO2007079969A1 true WO2007079969A1 (fr) 2007-07-19

Family

ID=38109108

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/012557 Ceased WO2007079969A1 (fr) 2006-01-09 2006-12-27 Soupape à tiroir longitudinal, en particulier pour l'utilisation de cycles de climatisation transcritiques au co2 (r 744)

Country Status (3)

Country Link
EP (1) EP1971809A1 (fr)
DE (1) DE102006001142B3 (fr)
WO (1) WO2007079969A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017107296A1 (de) * 2017-04-05 2018-10-11 Hanon Systems Absperrventil und Fluid-Absperreinrichtung eines Kältemittelverdichters
EP4603731A1 (fr) * 2024-02-16 2025-08-20 Thomas Magnete GmbH Unité de soupape

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008047311A1 (de) * 2008-09-16 2010-04-15 Mahle International Gmbh Ventileinrichtung
WO2015043637A1 (fr) * 2013-09-26 2015-04-02 Robert Bosch Gmbh Ensemble doseur
EP3358233B1 (fr) 2017-02-03 2020-09-30 SVM Schultz Verwaltungs-GmbH & Co. KG Soupape, en particulier soupape à tiroir

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1860447A (en) * 1928-07-21 1932-05-31 York Ice Machinery Corp Refrigeration
GB579391A (en) * 1942-12-18 1946-08-01 Packless Metal Products Corp Improvements in or relating to valves
US3136336A (en) * 1960-08-25 1964-06-09 Powers Regulator Co Valve
JPS5618169A (en) * 1979-07-20 1981-02-20 Keihin Seiki Mfg Co Ltd Valve device
DE3820525A1 (de) * 1988-06-16 1989-12-21 Opel Adam Ag Luftverteiler
DE10305947A1 (de) * 2003-02-12 2004-08-26 Robert Bosch Gmbh Expansionsorgan für eine Klimaanlage
DE10354229A1 (de) * 2003-11-20 2005-06-23 Robert Bosch Gmbh Expansionsventil
WO2005080889A1 (fr) * 2004-02-19 2005-09-01 Robert Bosch Gmbh Module d'expansion pour refrigerants

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4548238A (en) * 1983-12-19 1985-10-22 Chorkey William J Directional control valve with straight through flow
DE3534490A1 (de) * 1985-03-15 1986-09-18 Albrecht-Automatik GmbH & Co, 5024 Pulheim Hochdruckventil
DE4027610C2 (de) * 1990-08-31 1996-06-13 Festo Kg Ventil
DE4304440B4 (de) * 1993-02-13 2004-05-06 Steuerungstechnik Staiger Gmbh & Co. Produktions-Vertriebs-Kg Ventil
DE4416056C2 (de) * 1994-05-02 1998-03-19 Mannesmann Ag Wegeventil

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1860447A (en) * 1928-07-21 1932-05-31 York Ice Machinery Corp Refrigeration
GB579391A (en) * 1942-12-18 1946-08-01 Packless Metal Products Corp Improvements in or relating to valves
US3136336A (en) * 1960-08-25 1964-06-09 Powers Regulator Co Valve
JPS5618169A (en) * 1979-07-20 1981-02-20 Keihin Seiki Mfg Co Ltd Valve device
DE3820525A1 (de) * 1988-06-16 1989-12-21 Opel Adam Ag Luftverteiler
DE10305947A1 (de) * 2003-02-12 2004-08-26 Robert Bosch Gmbh Expansionsorgan für eine Klimaanlage
DE10354229A1 (de) * 2003-11-20 2005-06-23 Robert Bosch Gmbh Expansionsventil
WO2005080889A1 (fr) * 2004-02-19 2005-09-01 Robert Bosch Gmbh Module d'expansion pour refrigerants

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017107296A1 (de) * 2017-04-05 2018-10-11 Hanon Systems Absperrventil und Fluid-Absperreinrichtung eines Kältemittelverdichters
EP4603731A1 (fr) * 2024-02-16 2025-08-20 Thomas Magnete GmbH Unité de soupape

Also Published As

Publication number Publication date
EP1971809A1 (fr) 2008-09-24
DE102006001142B3 (de) 2007-06-28

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