WO2008000370A1 - Soupape de régulation pour des systèmes de climatisation r 744 - Google Patents

Soupape de régulation pour des systèmes de climatisation r 744 Download PDF

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Publication number
WO2008000370A1
WO2008000370A1 PCT/EP2007/005369 EP2007005369W WO2008000370A1 WO 2008000370 A1 WO2008000370 A1 WO 2008000370A1 EP 2007005369 W EP2007005369 W EP 2007005369W WO 2008000370 A1 WO2008000370 A1 WO 2008000370A1
Authority
WO
WIPO (PCT)
Prior art keywords
sealing
seat
sealing body
control valve
valve according
Prior art date
Application number
PCT/EP2007/005369
Other languages
German (de)
English (en)
Inventor
Axel MÜLLER
Rene Schulz
Johannes Alken
Bernd Köhler
Stefan Quast
Andreas Henke
Roger Klein
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
Publication of WO2008000370A1 publication Critical patent/WO2008000370A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/36—Valve members
    • F16K1/38—Valve members of conical shape
    • 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
    • F16K31/0603—Multiple-way valves
    • F16K31/0606—Multiple-way valves fluid passing through the solenoid coil
    • 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
    • F16K31/0655—Lift valves
    • F16K31/0658—Armature and valve member being one single element
    • 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
    • F16K31/0655—Lift valves
    • F16K31/0665—Lift valves with valve member being at least partially ball-shaped
    • 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 control valve for the refrigerant R 744 according to the preamble of claim 1.
  • Valves, z Such control valves are used as actuators in compressors with variable stroke and as an expansion device.
  • Valves, z. As electronically controllable, serve as essential actuators in the control loop of the air conditioning system. With their help, the refrigerant flow is metered in response to an electrical signal or a large pressure difference between valve inlet and outlet is set.
  • the R 744 circuit can be transcritically operated at high pressures and still be compact.
  • the actuators must be characterized by a very good pressure balance and have only very low internal leakage values.
  • characteristics should be adapted to the control task. That The opening cross section generated during the stroke should be able to be influenced accordingly depending on the flow rate. It is essential that the materials used have excellent compatibility with the refrigerant and the refrigerator oils used.
  • R 744 requires, in particular for the expansion valve, a pressure-resistant design of all its components to prevent external leakage of the refrigerant.
  • R 744 usually seals made of elastomeric material in the form of O-rings used.
  • the use of plastics and elastomers, however, is problematic for components in contact with R 744, since they tend to fail due to explosive decompensation due to the diffusion of R 744. External leakage is reduced by elastomeric sealing only, not avoided.
  • Valves with pressure-resistant magnet designs are known for brake valves. In conventional refrigeration systems for mobile applications thermostatically controlled expansion valves are used.
  • DE 103 05 947 A1 shows a slide seat valve in the application as
  • Expansion valve for air conditioning.
  • the valve works with a modification of the gap geometry between the valve piston as a slide element and the piston guide as the seat of the slide.
  • the arrangement operates essentially according to the valve principle of valves, whereby high leakage losses are implied.
  • DE 102 55 740 A1 shows a directly controlled proportional pressure relief valve, in which an actuating rod with a sealing body by means of an armature of a proportional solenoid is actuated.
  • the actuating rod is gimbal-mounted in the armature and guided in a housing-side leadership. Between the actuating rod and the housing-side guide and between the actuating rod and the armature, a radial clearance is provided, wherein the first game is less than the second game.
  • DE 100 27 171 A1 shows a solenoid valve with an actuating rod having an elastic axial portion between its attachment to the anchor rod and the seat disposed in a valve seat sealing body.
  • the attachment is accommodated at its end portion facing the valve seat in an additional guide sleeve with play, which is arranged concentrically to the valve seat in the valve housing.
  • the flexurally elastic portion allows a reduction of the transverse forces, the especially occur at the contact points of the magenta tanker with the valve sleeve.
  • DE 199 17 756 A1 shows a solenoid valve with a multi-part design of an actuator rod moved by the armature of the magnet and a sealing body of the valve whose parts are supported by a joint. Between the guide and the operating rod game is provided, whereby although a reduction in friction is generated by reducing lateral forces by an eccentric position of the components, however, this articulated connection does not affect the sealing function of the sealing body and its sealing seat.
  • DE 102 54 341 A1 shows a seat valve with an additional centering sleeve leading the valve tappet, which is hinged to the valve seat body. By this arrangement, the minimum radial clearance in the centering is to be reduced.
  • the valve seat body forms with the inner wall of the centering a hinge connection, comparable to a universal joint, which is either concave or convex. Again, no improvement of the sealing function is provided.
  • DE 41 37 123 A1 shows a pressure control valve with a variable
  • valve opening cross-section The valve stem is also guided in an additional guide member, in which radially movably arranged sealing elements are provided, into which the plunger is guided radially with play, and with which it is further pressed by self-centering in the valve seat.
  • the seat valves known from the valve technology do not fulfill the control quality for R 744 air conditioning circuits. You can not work with the high pressures that occur in the air conditioning circuit.
  • the object is achieved in combination with the preamble by the characterizing features of claim 1.
  • the proposed valve construction is characterized by very low internal
  • a self-centering of the two valve components is achieved regardless of the selected sealing body shape and contouring with the sealing seat.
  • the centering in the seat takes place on the one hand by an elastic or assembly-related alignment of the sealing body in the sealing seat (Materialelastizi- fact) and alternatively by a floating seat, the alignment of the sealing body is provided radially to the sealing seat.
  • the elastic and assembly-related alignment of the sealing body to the sealing seat is matched to the permissible closed position of the sealing body. This results in a mechanical decoupling of the sealing body acting in the radial direction from the actuating rod.
  • a function-dependent guide clearance to compensate for fit inaccuracies is provided between the guide bore and the actuating rod.
  • This game is designed so that the movement of the rod is not obstructed, but at the same time a leakage of the refrigerant R744 is minimized as possible. As a result, high demands on concentricity and centricity are no longer required.
  • the valve By designing the clearance between the pilot hole and the actuator Rod, the valve has a low hysteresis, since only small friction surfaces are present and they are optimally designed.
  • the guide is also designed for the best possible sealing, with a possible lowest possible sliding friction of the components is sought, taking into account the use of the valve as an actuator.
  • the sealing body and the seat can be structurally designed to ensure a very good seal with complete pressure compensation, i. the various components of the valve experience no additional force due to an applied pressure difference.
  • the guide bore of the actuating rod seals with the least possible friction in the best possible way in order to be able to adequately fulfill the task with the lowest possible hysteresis.
  • the sealing body and the seat center independently during closing of the valve.
  • a sealing diameter is determined with the corresponding seat contour. Due to the geometric design of the sealing body and the seat, a flow characteristic of the control valve is characterized.
  • the characteristic curve adaptation of the arrangement of the opening cross-section - stroke or the flow rate allows the valve to fulfill its role as a control element of a transcritical R 744 air conditioning circuit in an ideal way. It allows characteristic curves to be adapted to suit the task, especially in the area of fine control at low flow rates. This requires - in contrast to the known solutions - no additional slide valve with special opening contour, so that the valve can be both cost-effective and compact build because of the simple structure. The adjustment is not only at low
  • the diameter of the guide bore approximately corresponds to the effective diameter of the sealing body in the sealing seat.
  • Sealing body completely from the sealing seat, so as to open a much larger cross-sectional areas. This realizes a wider range of significantly higher flow rates.
  • valve has different flow characteristics of the refrigerant.
  • several, preferably two flow relationships can be combined in a single valve, so that the characteristics for the respective control task can be optimized.
  • the sealing geometry is designed so that with a small stroke of the actuating rod only a small change in the opening area occurs - this corresponds to a flat curve of the curve stroke - opening area - while the ratio opening area / stroke with larger Hub takes higher values.
  • the valve operates advantageously as a throttle valve with approximately progressive characteristic, since the effective throttle cross-section grows more than proportionally with the stroke of the valve.
  • the characteristic region extending in the progressive region is also achieved by adapting the geometry of the sealing body and the sealing seat.
  • the known relationship based on the flow laws for the refrigerant R 744 in the thermodynamic states at the valve inlet and outlet can be used. This relationship is based on an empirically verified theoretical description of the flow as a function of the geometry, so that different flow geometries can be derived therefrom for a corresponding geometry of the sealing body and the sealing seat. About that In addition, the requirements of the refrigerant and the materials that can be used for it must be included.
  • the design of the sealing body and valve seat is advantageously carried out so that the ratio opening surface stroke is variable over the stroke.
  • a sealing body with sections of different cone angle is used, alternatively contours can be introduced into the seat or sealing body, which are preferably applied mechanically (embossing, etc.) or chemically (etching, etc.).
  • the actuating rod has an elastic section extending in the axial direction, which extends between the sealing body and the actuating device, so that the sealing body can center itself in the seat.
  • the radial orientation of the sealing body can have an elastic region between the guide bore and the sealing body.
  • the centricity of the sealing body and seat is ensured, whereby the Diszentrizi- ity of the sealing body in the seat can be significantly improved.
  • the leadership of the operating rod seals with the least friction best possible to meet the task adequately as a control element with the lowest hysteresis.
  • the sealing seat can be arranged radially elastically displaceable in a further preferred embodiment. Only when it is closed by the sealing body, it is then fixed radially.
  • the sealing seat is designed so that the body itself is used as a guide for the seat. The seat is moved while until an optimal seal is achieved.
  • the seat can initially be performed radially floating, but then be set during assembly under constant measurement of the leakage in an optimal position. This setting takes place so that there is no radial displacement.
  • the actuating rod and the sealing body are a component.
  • the arranged in the direction of the inlet and outlet of the valve head of the rod is used as a sealing body in the form of a cylindrical body, for.
  • As a needle as a conical body in the form of a cone with a positive or alternatively negative negative cone angle or as a ball.
  • the sealing body may be designed as a separate component, which is loosely connected to the actuating rod.
  • the sealing body can also be slightly aligned with radial play to the seat.
  • the actuating rod acts in this case as a plunger.
  • Needle the sealing diameter with the corresponding seat is determined by the shape. Due to the geometric design of the needle and seat, as already explained above, the flow characteristic is characterized.
  • the needle may e.g. be purely cylindrically shaped or alternatively may have an additional cone or truncated cone at its tip.
  • the needle and seat are structurally designed so that a very good seal is ensured with complete pressure compensation, so that no additional force due to applied pressure differences occur.
  • the cylindrical end of the needle can be rounded so that a defined contact line is created between the sealing body and the seat.
  • a correspondingly shaped sealing cone can be attached to the needle point.
  • a conical body, a cone, with a positive or alternatively negative cone angle can be used as the sealing body.
  • the sealing diameter is determined together with the corresponding seat by the latter. Due to the geometric design of the sealing body and the seat, the flow characteristic can also be influenced in this embodiment.
  • the cone angle is executed with the smallest possible angle or paraboloid. The determination of the cone angle takes place in an optimization calculation which precludes an optimal design on the one hand the possible self-locking of the cone, On the other hand, however, allows the finest possible resolution of the signal behavior in the control process.
  • the complete emersion of the sealing cone from its seat is advantageously carried out at a positive cone angle, whereby the required wide range is achieved with significantly higher flow rates.
  • the structural design of the seat in the conical version is designed so that a very good seal is ensured without the occurrence of additional force effects due to applied pressure differences. This is achieved by rounding the seat so that a defined contact line is created between the sealing body and the seat. To achieve a complete pressure equalization, the diameter of the guide of the actuating rod is determined so that it corresponds to the actual sealing diameter. Consequently, the seat may also preferably be provided as separate components in this embodiment, or the actuating rod and the sealing cone may be designed as different components.
  • the seat may also be listed as a cone, which is blunter than the conical sealing body. This creates a perfect pressure equalization between the two valve parts.
  • the sealing cone has different cone angles in sections.
  • a pointed cone is required for a small stroke, while a blunt cone is required for a long stroke.
  • the sealing body may be designed as a ball, wherein the sealing diameter is fixed together with the corresponding seat by the latter. Due to a geometric design of the seat, the flow characteristic can be influenced.
  • the ball can be pressed either against a spring by the actuating rod designed as a plunger or the ball is held by means of the force of the spring in the open state and pressed by the force of the actuator.
  • the seat meets the requirements for a good seal and as possible no additional force due to applied pressure differences, two variants of the sealing contour can be realized constructively.
  • the seat can be made rounded, so that a defined contact line between the sealing body and the seat is formed, on the other hand, the seat can be made sharp-edged without rounding or conical bevel.
  • the control valve is designed as a solenoid valve.
  • the actuating device comprises a proportionally operating lifting magnet with a pushing armature piston, at whose front side facing the inflow and outflow the actuating rod extends in the axial direction. It is a 2/2-way valve throttle valve, whereby the sealing body can work in both the "normally open” and "normally closed” versions.
  • Fig. 1 shows a cross-sectional view of the invention
  • FIG. 2 shows a detail from FIG. 1
  • Fig. 3 shows a schematic diagram of the execution as a needle valve
  • Fig. 4 shows the illustration of Fig. 3 in a dipping position of the needle valve.
  • Fig. 5 shows a schematic diagram of the execution as a conical seat valve with a negative cone angle.
  • Fig. 6 shows a variant of Fig. 5 with rounded seat.
  • FIG. 7 shows conical contours for characteristic curve influencing in a schematic diagram.
  • Fig. 8 shows a schematic diagram of the execution as a ball valve.
  • 1 shows a schematic diagram in the form of a longitudinal cross-section through an inventive control valve 1, which is used as an expansion element or as a valve of a multi-evaporator - air conditioning system in an air conditioner application.
  • the control valve 1 serves to regulate the high pressure in a transcritical CO 2 air conditioning cycle in mobile applications. This happens because the refrigerant in the expansion valve 1 is selectively throttled to a lower pressure (expansion element). The internal pressure of the refrigerant is thereby reduced in an isenthalpic expansion.
  • the valve 1 has an inlet and a drain 2 in the form of channels, the connection of which can be opened or closed in the desired manner via a sealing body 3a and sealing seat 3b, wherein intermediate positions can also be regulated analogously.
  • Inlet or outlet 2 respectively form the high and low pressure side of the valve 1, depending on the direction of the refrigerant. Since the valve can be flowed through bidirectionally, the inlet and the outlet 2 each have the same reference numerals. The throttling of the refrigerant takes place inside the valve.
  • the valve functions are actuated electromagnetically by a cup-shaped electromagnet 4 shown in the right-hand area of FIG. 1 by means of a reciprocating piston 5, which is driven by an externally arranged magnetic coil 6 with yoke 24, which are acted upon by a plug element 7 with a corresponding drive signal.
  • the electromagnet 4 forms the actuating device 17 for the valve 1.
  • the electromagnet 4 is surrounded by a flux-conducting housing 8, in which a magnetic coil 6 and the plug element 7 are integrated, with which the magnet 4 is energized.
  • the housing 8 thus forms a space which is closed inwardly by a coaxial with the axis of the armature piston 5 cup-shaped sleeve 9, which serves as a guide for the Hubbewe- movement of the armature 5, wherein the open end of the sleeve 9 in the direction of the lifting movement of the armature 5 is arranged.
  • the bottom of the case is spherical is executed.
  • the electromagnet 4 is closed at its right end by a stroke limiter 12 for the spherical sleeve bottom.
  • the open end of the sleeve 9 is mounted directly on the outer wall of the control cone 10 of the electromagnet 4, wherein the control cone 10 and the associated pole 13 are in turn part of a valve block 11, in which all valve functional means of the expansion valve 1 are integrated.
  • Control cone 12 and pole 13 thus form an adapter for the valve block 11.
  • the cone 12 When the valve block 11 is made of a non-magnetic material, the cone 12 must be made of magnetizable material and, other than shown in FIG. 1, as a separate part. It is then joined to the valve block 11 and sealed separately.
  • the sleeve 9 of the electromagnet 4 and the valve block 11 are designed as separate components, which are joined via a junction pressure and free of leakage.
  • both components can also be designed as a compact unitary component that does not require a joint.
  • connection between sleeve 9 and control cone 10 is preferably cohesively. This not only creates a pressure-resistant anchor interior, but also a safe external leakage-free valve interior. In this way, can be dispensed with an - additional, for example, elastomeric - sealing the armature space by means of O-rings, so that the assembly can be simplified and carried out process reliable.
  • the armature piston 5 has the pressure relief during the stroke in the axial (18 a) and radial (18 b) direction extending holes. At the arranged in the direction of the control cone 10 end face of the armature piston 5 projects in the axial direction of an actuating rod 23 for the arranged at the other end sealing body 3a.
  • the valve block has an axial through bore 25 into which the actuating rod 23 is guided.
  • the valve block 11 has a further through-bore 21 parallel to the guide bore 25.
  • the valve 1 comprises several seals in the form of O-rings.
  • the first O-ring seal 14 seals off the flux-guiding housing 8 from the armature interior of the electromagnet 4, another seal 14 seals off the junction of the housing with the valve block 11, which in turn is sealed off from the outside world by a further pair of O-ring seals 20.
  • the region of the valve block 11, which comprises the inlet and outlet 2 with the sealing body 3a and the sealing seat 3b, is shown enlarged in FIG.
  • the sealing seat 3b is designed in the representation of FIG. 2 as a radial disc whose axial extent comprises the sealing contour 27 with that of the sealing body 3a, which is provided with the reference numeral 28.
  • the sealing seat 3b is designed in the representation of FIG. 2 as a separate component, which is arranged radially floating, whereby an elastic or assembly-related radial alignment of the sealing body 3a is provided to the sealing seat 3b. He is thus initially stored radially with clearance and then radially fixed at closure by the sealing body 3a.
  • the sealing body 3a has in Fig.
  • FIGS. 2 In addition to the conical shapes of the sealing body 3a shown in FIG. 2, further variants of the sealing body and the associated sealing seat 3b are shown in FIGS. For simplicity, only schematic diagrams of the different design of the sealing body 3a are shown, wherein the same functions are provided with the same reference numerals.
  • Fig. 3 shows the variant of the sealing body 3a as a cylindrical body which defines a needle 30, which - due to their shape - a sealing diameter 38 (see also Fig. 8) with the corresponding sealing seat 3b.
  • the needle 30 has at its tip an additional truncated cone 31, whereby the flow characteristic of the valve 1 can be characterized.
  • the sealing contour 27, 28 of both the Dichtgropers 3a and 3b of the seat are parallel, so that a complete contact of the two contours is ensured at closure.
  • the needle 30 is separated as a separate component from the actuation rod 23, not shown in FIG. 3, which in this case acts like a plunger 40 (see also FIG. 8) on the rear end of the needle 30 when activated.
  • a compression spring 32 is provided as a counterforce for the magnetic force acting on the needle 30.
  • the compression spring 32 is provided at the rear end of the needle 30 on a holder 33 coaxially around the needle 30 is arranged and is supported in an axial recess 34 of the guide bore 25.
  • FIG. 4 shows the embodiment of Fig. 3 with a blunt needle point, wherein the needle 30 is completely out of the seat 3b, whereby a significantly larger cross-sectional area is opened.
  • the diameter of the guide bore 25 is almost equal to the sealing diameter 38 on the seat 3b.
  • Fig. 5 to Fig. 7 are schematic diagrams of the sealing body 3a with its seat 3b as a conical body, wherein the sealing diameter 38 (see Fig. 8) is fixed together with the corresponding seat by the seat 3b.
  • the geometric configuration of the sealing body 3a and the seat 3b influences the flow characteristic.
  • the sealing body 3a in Fig. 5, as the illustration in Fig. 2 designed as a cone 35, but here with a negative cone angle, the cone 35 is designed with a small amount angle.
  • the seat 3b a rounding 36 of its sealing contour 27. It is - as already mentioned in the description of FIG. 2, designed as a separate component, which is inserted into the flat spring insert 26 (see FIG. 2) and is mounted radially with play.
  • FIG. 7 in the left-hand illustration, a sealing body / sealing seat arrangement with a curved contour 27, 28 is sketched both for the sealing body 3a and for the sealing seat 3b, the curvature between the two contours being different.
  • the right-hand illustration shows an arrangement of a sealing body contour 27 with different pitches, which abuts against a rectangular sealing seat edge 38.
  • a ball 39 was used as a sealing body 3a, wherein the sealing diameter 38 is fixed together with the sealing seat 3b by the latter.
  • the diameter of the guide bore 25 corresponds to that of the sealing diameter 38.
  • the seat 3b is provided as a separate component.
  • the actuating rod 23 has at its end facing the ball 39 a plunger 40, so that the sealing body 3a and the actuating rod 23 are different components.
  • the invention has been explained with reference to an acting as an actuator electromagnet. Besides this form of activation, activation by other types of actuators also belongs to the invention. It is not limited to the embodiments described above, but is often variable within the scope of the disclosure. All new, in the description and / or the drawing disclosed individual and combination features are considered essential to the invention.

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

Abstract

L'invention concerne une soupape de régulation pour le fluide réfrigérant R744 en vue de réguler une forte différence de pression entre une alimentation et une évacuation (2) du fluide réfrigérant dans la soupape (1) comprenant un dispositif d'actionnement (17). Dans un alésage de guidage (25) agencé dans la soupape 1 et s'étendant dans le sens axial, le dispositif d'actionnement actionne une tige d'actionnement (23) qui comporte un corps d'étanchéité (3a) à son extrémité tournée vers l'alimentation et l'évacuation (2). Le corps d'étanchéité (3a) ouvre et/ou ferme par un mouvement de levage de la tige d'actionnement (23) son siège d'étanchéité (3b) et ainsi son alimentation et son évacuation (2), un jeu de guidage fonctionnel minime étant prévu entre l'alésage de guidage (25) et la tige d'actionnement (23) afin de compenser les inexactitudes d'ajustement. L'invention est caractérisée en ce qu'il est prévu une orientation, élastique ou radiale déterminée par le montage, du corps d'étanchéité (3a) vers le siège d'étanchéité (3b), ladite orientation étant adaptée à la position de fermeture admissible du corps d'étanchéité (3b), le siège d'étanchéité étant logé lors du montage dans un premier temps radialement avec du jeu et ensuite fixé radialement lors de la mise en place du corps d'étanchéité (3a).
PCT/EP2007/005369 2006-06-26 2007-06-19 Soupape de régulation pour des systèmes de climatisation r 744 WO2008000370A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006029267.7 2006-06-26
DE102006029267A DE102006029267B4 (de) 2006-06-26 2006-06-26 Regelventil für R 744-Klimasysteme

Publications (1)

Publication Number Publication Date
WO2008000370A1 true WO2008000370A1 (fr) 2008-01-03

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PCT/EP2007/005369 WO2008000370A1 (fr) 2006-06-26 2007-06-19 Soupape de régulation pour des systèmes de climatisation r 744

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DE (1) DE102006029267B4 (fr)
WO (1) WO2008000370A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009022974A1 (de) 2009-05-28 2010-12-09 Thomas Magnete Gmbh Elektromagnetisch betätigtes Schnellschaltventil als Einlassventil einer hydraulischen Antriebseinheit
DE102009053216A1 (de) * 2009-11-06 2011-05-12 Ipgate Ag Druckentlastetes 2/2-Wege-Schnellschaltmagnetventil
DE102009057183A1 (de) 2009-12-05 2011-06-09 Institut für Luft- und Kältetechnik gemeinnützige Gesellschaft mbH Elektrisch ansteuerbares Dosierventil
DE102013009095B4 (de) 2013-05-28 2015-11-26 Thomas Magnete Gmbh Hubkolbenpumpe mit einem Auslassventil geringer Baulänge sowie Verfahren zum Zusammenbau einer solchen
DE102014107279A1 (de) * 2014-05-23 2015-11-26 Otto Egelhof Gmbh & Co. Kg Expansionsventil
DE102015109077A1 (de) * 2015-06-09 2016-12-15 Kendrion (Villingen) Gmbh Volumenstromgeregeltes Sitzventil

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GB1213659A (en) * 1966-12-27 1970-11-25 Seram Sa Solenoid-actuated valve
FR2204280A5 (fr) * 1972-10-25 1974-05-17 Applic Gaz Sa
JPS59175680A (ja) * 1983-03-25 1984-10-04 Sugino Mach:Kk 高圧逃し弁
DE4137123A1 (de) 1991-11-12 1993-05-13 Teves Gmbh Alfred Drucksteuerventil
DE19625349A1 (de) 1996-06-25 1998-01-02 Rexroth Mannesmann Gmbh Magnetbetätigtes Sitzventil
DE19917756A1 (de) 1998-07-06 2000-01-13 Continental Teves Ag & Co Ohg Elektromagnetventil
DE10027171A1 (de) 2000-02-23 2001-08-30 Continental Teves Ag & Co Ohg Elektromagnetventil
DE10254341A1 (de) 2002-05-02 2003-11-20 Continental Teves Ag & Co Ohg Sitzventil
DE10255740A1 (de) 2002-11-28 2004-06-09 Bosch Rexroth Ag Direktgesteuertes prop. Druckbegrenzungsventil
DE10305947A1 (de) 2003-02-12 2004-08-26 Robert Bosch Gmbh Expansionsorgan für eine Klimaanlage
US20050189509A1 (en) * 2004-02-27 2005-09-01 Yuri Peric Leak-resistant solenoid valves

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2361398B1 (de) * 1973-12-10 1975-03-13 Danfoss A/S, Nordborg (Daenemark) Magnetventil mit Federn
DE19611832B4 (de) * 1996-03-26 2004-04-15 Continental Teves Ag & Co. Ohg Sitzventil

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1213659A (en) * 1966-12-27 1970-11-25 Seram Sa Solenoid-actuated valve
FR2204280A5 (fr) * 1972-10-25 1974-05-17 Applic Gaz Sa
JPS59175680A (ja) * 1983-03-25 1984-10-04 Sugino Mach:Kk 高圧逃し弁
DE4137123A1 (de) 1991-11-12 1993-05-13 Teves Gmbh Alfred Drucksteuerventil
DE19625349A1 (de) 1996-06-25 1998-01-02 Rexroth Mannesmann Gmbh Magnetbetätigtes Sitzventil
DE19917756A1 (de) 1998-07-06 2000-01-13 Continental Teves Ag & Co Ohg Elektromagnetventil
DE10027171A1 (de) 2000-02-23 2001-08-30 Continental Teves Ag & Co Ohg Elektromagnetventil
DE10254341A1 (de) 2002-05-02 2003-11-20 Continental Teves Ag & Co Ohg Sitzventil
DE10255740A1 (de) 2002-11-28 2004-06-09 Bosch Rexroth Ag Direktgesteuertes prop. Druckbegrenzungsventil
DE10305947A1 (de) 2003-02-12 2004-08-26 Robert Bosch Gmbh Expansionsorgan für eine Klimaanlage
US20050189509A1 (en) * 2004-02-27 2005-09-01 Yuri Peric Leak-resistant solenoid valves

Also Published As

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DE102006029267A1 (de) 2008-01-03
DE102006029267B4 (de) 2009-07-30

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