EP4256253A1 - Dispositif de soupape - Google Patents

Dispositif de soupape

Info

Publication number
EP4256253A1
EP4256253A1 EP21820252.1A EP21820252A EP4256253A1 EP 4256253 A1 EP4256253 A1 EP 4256253A1 EP 21820252 A EP21820252 A EP 21820252A EP 4256253 A1 EP4256253 A1 EP 4256253A1
Authority
EP
European Patent Office
Prior art keywords
expansion
valve element
fluid
section
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.)
Withdrawn
Application number
EP21820252.1A
Other languages
German (de)
English (en)
Inventor
Philipp Eichhorn
Jan Schlegel
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.)
Robert Bosch GmbH
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
Priority claimed from DE102021213523.4A external-priority patent/DE102021213523A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP4256253A1 publication Critical patent/EP4256253A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • 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
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/04—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having cylindrical surfaces; Packings therefor
    • F16K5/0407—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having cylindrical surfaces; Packings therefor with particular plug arrangements, e.g. particular shape or built-in means
    • 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
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
    • F16K5/0605—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor with particular plug arrangements, e.g. particular shape or built-in means
    • 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
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/08—Details
    • F16K5/12—Arrangements for modifying the way in which the rate of flow varies during the actuation of the valve

Definitions

  • the invention relates to a valve device and a valve element for a valve device according to the species of the independent claims.
  • Valves for controlling a fluid flow are already known.
  • DE 10 2017 208 181 A1 discloses a valve with a recess on the surface.
  • the present invention relates to a valve device, in particular an expansion valve for regulating a fluid flow of a fluid, in particular for a refrigerant circuit of a vehicle, having a valve element housing and a valve element arranged in the valve element housing, the valve element having a control passage and at least one expansion recess.
  • the expansion recess has a first expansion section, the first expansion section having an essentially constant flow cross section along the flow direction.
  • the valve device according to the invention with the features of the independent claim advantageously enables the smallest opening cross section to be set more precisely and reliably.
  • the expansion recess is shaped in such a way that it can provide a constant cross-section at the beginning, whereby the smallest opening is independent of tolerances and hysteresis. In this way, the smallest flow cross sections can be set reliably and safely.
  • a substantially constant flow cross section can be understood to mean, in particular, a surface through which the fluid flows, which does not change or changes only insignificantly over the entire longitudinal direction of the flow.
  • the term fluid is understood to mean a medium which, depending on the prevailing thermodynamic conditions, can be present both in a liquid phase and in a gaseous phase.
  • a fluid of the type in question is a heat transfer medium which circulates within the fluid circuit.
  • the fluid is a natural refrigerant such as hydrocarbons, carbon dioxide, ammonia, propane, butane, propene, water or a synthetic refrigerant such as chlorofluorocarbons or hydrofluorocarbons.
  • a control passage can be understood to mean an opening in the valve element, through which a main volume flow of the fluid can preferably flow.
  • the control passage preferably has an opening cross section which is many times larger than the average flow cross section of the expansion recess.
  • the first expansion section preferably extends over a circumferential angle of between 5° and 15°, preferably between 8° and 12°, particularly preferably essentially over 10° of the valve element.
  • the valve element has a second expansion section, with the flow cross section of the second expansion section increasing along the flow direction, in particular continuously increasing, with the second expansion section preferably directly adjoining the first Expansion section adjacent.
  • the first expansion section and the second expansion section together cover a circumferential angle of approximately 90°.
  • the control passage is preferably designed as a through hole through the valve element.
  • the control passage preferably passes through the valve element in the middle.
  • the control passage preferably leads from one side of the valve element to the diametrically opposite side of the valve element.
  • the control passage is preferably designed to be essentially straight, particularly preferably essentially free of projections.
  • the flow cross section of the control passage is preferably a multiple, preferably more than 20 times, larger than the flow cross section of the first expansion section.
  • the valve element has a first expansion recess and a second expansion recess, the expansion recesses being arranged on opposite passage openings of the control passage, in particular being arranged diametrically opposite one another on the valve element.
  • the expansion recesses are preferably designed to be essentially congruent in shape, in particular with the same shape. In this way, the same section of the expansion recess can be in contact with the fluid inlet or fluid outlet at the fluid inlet of the valve element housing and at the fluid outlet of the valve element housing.
  • the expansion recess and the control passage are designed to be fluidically connected to one another, with the expansion recesses and the control passage preferably being arranged within the valve element.
  • the valve element is preferably mounted such that it can rotate about an axis of rotation and has a rotationally symmetrical base body, preferably a spherical or cylindrical base body.
  • the control passage preferably has a first passage opening and a second passage opening along the direction of flow, with the expansion recess being arranged in the region of a passage opening of the control passage.
  • the first expansion section is spaced further from the passage opening than the second expansion section, the second expansion section preferably being fluidically connected to the control passage.
  • the valve element housing has at least one first fluid opening and at least one second fluid opening for a flow of a fluid stream, the fluid openings being fluidically connected to an inner volume arranged in the interior of the housing, the inner volume between the valve element and the valve element housing is formed, wherein the first fluid opening is formed as a fluid inlet and the second fluid opening is formed as a fluid outlet.
  • the first expansion section of the expansion recess is designed as a first expansion groove, in particular as a trough-shaped expansion groove in the lateral surface of the valve element.
  • the expansion groove preferably has a substantially rectangular cross-section.
  • the area through which flow occurs within the first expansion section is designed to be essentially constant, regardless of the circumferential angle.
  • the first expansion section designed as an expansion groove has a constant cross section over its entire extent in the direction of longitudinal extent, that is to say in the direction of flow.
  • the first expansion section of the first expansion recess is therefore preferably fluidically connected to the fluid inlet and the second expansion section of the second expansion recess is fluidically connected to the fluid outlet, with the control passage being arranged entirely in the interior volume of the valve element housing.
  • valve element can be rotated about an axis of rotation and the valve element has a rotationally symmetrical base body, preferably a spherical or cylindrical base body.
  • a valve element can be manufactured particularly easily and inexpensively.
  • the valve element preferably has an engagement which enables interaction with a valve stem moved by the electric drive.
  • a valve element can in particular also be understood to mean a valve means or a valve body.
  • the valve element is preferably arranged in a rotationally fixed manner on a valve stem.
  • the valve element is movably, preferably rotatably, arranged within the valve element housing. Depending on the position of the valve element, in particular the rotational position within the valve element housing, the valve element allows flow through the valve device, wherein the fluid flow can be expanded or compressed depending on the valve position and the flow direction, or can flow through the valve device unhindered.
  • valve element has a second expansion section, with the flow cross section of the second expansion section increasing, in particular continuously increasing.
  • the expansion recess preferably consists of a first expansion section and a second expansion section.
  • the flow area of the first expansion section is smaller than the average flow area of the second expansion section. In this way, tolerances of the drive element can be better compensated, particularly in areas with small flow diameters.
  • control passage has a first passage opening and a second passage opening along the direction of flow.
  • each of the passage openings is assigned an expansion recess.
  • each of the Passage openings are each formed fluidically directly connected to an expansion recess.
  • the first expansion section is preferably formed at a greater distance from the through-opening than the second expansion section.
  • the valve preferably has a separating element which is designed to fluidly separate the expansion recess and the control passage from one another within the valve element.
  • a separating element can be understood to mean an element which is designed to be essentially impermeable to a fluid of the type in question here.
  • the separating element is preferably designed to be liquid-impermeable.
  • a particularly preferred embodiment of the invention provides that the separating element inside the valve element is also designed to be gas-impermeable.
  • a gas-permeable valve element can be understood to mean a separating element which only permits a leakage rate of less than 10" 7 mbar/s, preferably less than 10" 8 mbarl/s, particularly preferably less than 5*10 -8 mban's .
  • This leakage rate corresponds approximately to a leak diameter of 0.4 pm per 2 mm wall thickness and an average gas loss of approximately 3 cm 3 of gas per year, with the leakage rate being able to be determined quantitatively using a test gas leak detector, for example.
  • Helium or hydrogen forming gas is preferably used as the test medium.
  • the separating function of the separating element is provided within the valve element.
  • the separating element interrupts the fluidic connection between the expansion recess and the control passage.
  • the separating element fluidly separates the expansion recess from the control passage volume in the sense of a blocking element. In order to test the separating function of the separating element within the valve element, it is therefore advantageous to essentially prevent a flow path outside the inner volume of the valve element.
  • a particularly preferred embodiment of the invention provides that the valve element has at least two expansion recesses, the expansion recesses being in opposite passage openings are arranged, in particular are arranged diametrically opposite one another on the valve element.
  • An advantageous development of the invention provides that the control passage has a first passage opening and a second passage opening along the direction of flow.
  • a particularly preferred embodiment of the invention provides that in a minimum flow position, which corresponds to a first valve position, the first expansion section of a first expansion recess is fluidly connected to a fluid inlet and the first expansion section of the second expansion recess is fluidly connected to a fluid outlet and the passage openings of the control passage are arranged entirely in the inner volume.
  • a sealing seat is arranged at the fluid inlet and/or at the fluid outlet.
  • the fluid inlet and/or the fluid outlet is essentially cylindrical.
  • the sealing seat preferably has an essentially cylindrical inner surface, which is arranged in the area of the opening. The flow resistance to the flowing fluid is thus minimized.
  • An advantageous development of the invention provides that at least one expansion recess, preferably all expansion recesses, extends in a radial plane perpendicular to the axis of rotation, the expansion recess preferably being arranged in a plane of symmetry of the valve element.
  • An advantageous development of the invention provides that the expansion recess is designed as an expansion groove in a lateral surface of the valve element. It is advantageous that the expansion recess is formed on the surface of the valve element.
  • Such a recess which is open at least on one side, advantageously enables simple regulation of the fluid flow through the inner volume of the valve element housing in the expansion position of the valve device.
  • a special low-pressure-loss valve can be provided in particular by the fact that the fluid inlet and fluid outlet are essentially aligned.
  • the fluid can thus flow through the valve, starting from the fluid inlet to the fluid outlet, through the straight control passage opening unhindered, uncompressed and straight. Pressure losses are significantly reduced.
  • the control orifice preferably extends centrally through the centerline of the valve member.
  • the valve element has precisely one control passage, the control passage being essentially straight.
  • the control passage is essentially free of curvature, in particular without projections and deflections. Due to the straight design of the control passage, pressure losses when flowing through the control passage can be prevented in an advantageous manner.
  • a particularly simple, flow-optimized passage can be provided in that the control passage is designed as a through hole through the valve element.
  • a particularly simple, small valve can be provided in particular by arranging the fluid openings of the valve element housing in a common radial plane. Inflow pipes or inflow flanges, which are mounted on the fluid openings, are therefore advantageously all in one plane.
  • Such a valve device can be designed to be significantly more space-saving.
  • the axes of symmetry of the fluid openings and the axis of rotation of the valve element preferably meet at a common center point.
  • FIG. 1 is a perspective view of a valve housing element 12,
  • Figure 2 shows a schematic representation of a section through a valve device in a minimum flow position 51
  • Figure 3 shows an enlarged section of a valve device in a minimum flow position 51 according to Figure 2
  • FIG. 4a-b Course of the angular positions of a valve device
  • FIG. 1 shows a first embodiment of a valve device 10 according to the invention in a perspective view.
  • the valve device 10 has an essentially cuboid housing, which is designed as a valve element housing 12 for a valve element 14 (not shown here).
  • the valve element 14 is movably mounted, in particular rotatably relative to the valve element housing 12 about an axis of rotation 18 extending essentially in the axial direction 16 .
  • the valve element housing 12 has an interior cavity 20 in which the valve element 14 is arranged when the valve device 10 is in the assembled state. In the assembled state, an internal volume 26 through which a flow can flow remains in the cavity 20 between the valve element 14 and the valve element housing 12.
  • the valve element housing 12 has two fluid openings 22a, 22b. The fluid openings 22a, 22b are designed as through-openings through the housing wall of the valve element housing 12.
  • the fluid openings 22a, 22b are designed as through holes. It is also conceivable that a valve device of the type in question has more than two fluid openings 22a, 22b.
  • the fluid opening 22a is designed as a fluid inlet 23a and the fluid opening 22b is designed as a fluid outlet 23b and the opening 22c is designed as a fluid outlet 23c.
  • the Fluid openings in a plane, the radial plane 24 arranged. The fluid inlet 22a and the fluid outlet 22b are arranged in alignment.
  • a sealing seat is arranged at least in the area of a fluid opening 22a.
  • the sealing seat is preferably designed as a sealing ring, which is arranged in the opening cross section of the at least one opening 22a, 22b.
  • the sealing seat is preferably arranged in a region of the at least one fluid opening 22a, 22b that faces the inner volume 26 and essentially completely encloses the fluid opening 22a, 22b in the circumferential direction.
  • the first fluid opening 22a has a first sealing seat 27a and the second fluid opening 22b has a second sealing seat 27b. It is also conceivable that all fluid openings 22a, 22b each have a corresponding sealing seat 27a, 27b.
  • the valve element housing 12 has a passage 31 for a valve stem 32, which is driven by an electric drive.
  • the valve element 14 is arranged on the valve stem 32 .
  • the valve stem 32 passes through the passage 31 of the valve element housing 12 and extends essentially in the axial direction 16.
  • the valve element housing 12 is designed as a valve center block.
  • Such a valve center block is preferably made of aluminum or an aluminum alloy.
  • FIG. 2 shows the sectional view of a valve device 10 along the radial plane 24 in a minimum flow position 51.
  • the valve element housing 12 has two opposite fluid openings 22a, 22b.
  • the fluid opening 22a is designed as a fluid inlet 23a and the fluid opening 22b is designed as a fluid outlet 23b.
  • the fluid inlet 23a and the fluid outlet 23b are arranged in a radial plane 24.
  • Fluid inlet 22a and fluid outlet 22b are preferably aligned with one another.
  • the sealing seats 27a, 27b are not shown in FIG. 2 for reasons of clarity.
  • sealing seats 27a, 27b are arranged at the fluid inlet 23a and at the fluid outlet 23b.
  • the sealing seats are preferably in each case on the side of the fluid inlet 23a and of the fluid outlet 23b facing the inner region 26 .
  • the sealing seats 27a, 27b are designed here, for example, as sealing rings, which are arranged in the opening cross section of 22a, 22b.
  • the sealing seats 27a, 27b are arranged in an area facing the inner volume 26 and enclose the corresponding fluid opening 22a, 22b in the circumferential direction.
  • the valve device 10 has a valve element 14 which has an essentially spherical base body 38 .
  • the valve element 14 is designed to be movable, in particular rotatable relative to the valve element housing 12 .
  • the first valve means housing 12 has an internal volume 26 through which a fluid can flow.
  • a fluid of the type in question is preferably a heat transfer medium which circulates within the fluid circuit.
  • the fluid is a natural refrigerant such as hydrocarbons, carbon dioxide, ammonia, propane, butane, propene, water or a synthetic refrigerant such as chlorofluorocarbons or hydrofluorocarbons.
  • a valve element housing 12 of the type in question can be designed in particular as a valve center block which is designed to be essentially gas-tight due to the thermodynamic conditions prevailing in an expansion valve.
  • the fluid in the flowable inner volume 26 of the valve element housing 12 is at least partially in a gaseous phase, with high pressures in the range between 1-30 bar and briefly up to 100 bar prevailing.
  • the valve element housing 12 made of a metal, preferably aluminum or Aluminum alloy be formed.
  • at least one housing part of the valve element housing 12 has a plastic body with a diffusion-inhibiting barrier layer containing metal.
  • valve element housing 12 can be manufactured simply and inexpensively in comparison to an aluminum block housing. At the same time, due to the gas-tightness of the valve device, it can be used in fluid circuits in which the fluid is at least partially in a gaseous phase.
  • the valve element 14 has a control passage 30 .
  • the control passage 30 has two passage openings 34, 36 along the direction of flow.
  • the passage openings 34, 36 are arranged on the lateral surface of the valve element 14, the second passage opening 36 being arranged upstream of the first passage opening 34.
  • the openings 22a, 22b preferably each have identical inside diameters.
  • the fluid openings preferably have a common axis of symmetry.
  • the control passage 30 is preferably designed as a through opening, in particular as a through bore. In order to avoid flow losses, according to an advantageous development of the invention, the control passage 30 is designed to be essentially straight.
  • First passage opening 34 and second passage opening 36 are preferably arranged diametrically aligned with one another.
  • the inner wall of the control passage 30 is preferably designed without any curvature or projections.
  • the valve element 14 preferably has no further opening cross sections for a fluid flow.
  • the valve element 14 has precisely one control passage 30 .
  • the axis of rotation 18 extends perpendicularly to the radial plane 24 in which the fluid openings 22a, 22b are arranged.
  • the valve element 30 has at least one expansion recess 40 .
  • the valve element 14 has a first expansion recess 40a and a second expansion recess 40b.
  • the expansion recesses 40a, 40b are preferably arranged diametrically opposite one another. According to the embodiment of the invention illustrated in FIG.
  • expansion recesses 40a, 40b are each in the form of a surface notch.
  • the expansion recesses 40a, 40b preferably have a substantially channel-shaped contour.
  • the expansion recesses 40a, 40b preferably each extend along an imaginary circular line on the lateral surface 44 of the essentially spherical valve element 14.
  • the expansion recesses 40a, 40b preferably extend on average a few millimeters deep into the valve element 14.
  • the expansion recesses 40a, 40b are preferably formed in particular as channel-shaped elements each have a substantially rectangular cross-section. However, other cross-sectional shapes are also conceivable. It is also conceivable, for example, for the expansion recesses 40a, 40b to have essentially rounded edges.
  • the expansion recesses 40a, 40b are designed to be congruent in shape to one another.
  • FIG. 2 shows a valve device in a minimum passage position 51.
  • the expansion recesses 40a, 40b preferably each have a first expansion section 60a, 60b. It is also conceivable that only one of the expansion recesses has such a first expansion section 60a, 60b.
  • the first expansion section 60a, 60b is designed as a minimum passage. It therefore preferably has the smallest possible flow cross section within the valve element 14 . According to the invention, it is now provided that the first expansion section 60a, 60b over its entire extent, in particular over its entire extent in the circumferential direction on the lateral surface of the spherical Valve element 14 has a substantially constant cross section.
  • the expansion recesses 40a, 40b thus each have a constant, minimum cross section in their initial area, ie in an area at a maximum distance from the respective passage opening 34, 36.
  • a second expansion section 66a, 66b follows each of these first expansion sections 60a, 60b, which is designed as a constant cross-sectional area, the cross section of which increases continuously in the direction of the passage openings 34, 36.
  • FIG. 2 now shows a valve position, the minimum passage position 51, in which the valve element 14 is set in such a way that the first expansion sections 60a, 60b each bear against the fluid inlet 23a and the fluid outlet 23b.
  • the fluid flowing through the valve device 10 is now conducted through the cross sections of the first expansion sections 60a, 60b.
  • FIG. 3 shows an enlarged representation of the first expansion recess 40a.
  • the first expansion section 60a, 60b preferably extends over a circumferential angle 64 of between 5° and 15°, preferably between 8° and 12°, particularly preferably essentially over 10° of the valve element.
  • the valve element can thus be rotated through an angle between 5° and 15°, preferably between 8° and 12°, particularly preferably essentially more than 10°, while the valve device is in a minimum passage position 51 .
  • Such a long first expansion section 60a, 60b in the direction of flow, which has a constant flow cross section makes it possible to set the smallest opening cross section more precisely and reliably.
  • the first expansion section 60a, 60b allows small flow cross sections to be provided essentially independently of tolerances and hysteresis.
  • a second expansion section 66a, 66b follows the first expansion section 60a, 60b.
  • the first expansion section 60a and the second expansion section 66a of an expansion recess 40a, 40b preferably each jointly cover a circumferential angle of approximately 90°.
  • the second expansion section 66a, 66b thus preferably covers a larger one circumferential angle than the first expansion section 60a, 60b.
  • the second expansion section 66a, 66b connects to the control passage 30.
  • the control passage 30 is fluidly connected to the second expansion sections 66a, 66b.
  • the first expansion section 40a has a constant flow cross section over the entire circumferential angle 64 as a surface function depending on the groove depth 62 and groove width 63 (not shown here). According to a particularly advantageous development of the invention, it can be provided that both the groove depth 62 and the groove width 63 are designed to be essentially constant.
  • FIG. 4a shows four different valve positions.
  • FIG. 4b shows the course of the opening cross-sections for the throughflow of the fluid corresponding to these valve positions (items 1-4).
  • Position 1 shows a position in which the respective first expansion sections 60a, 60b are fluidly connected to the fluid inlet 23a and the fluid outlet 23b.
  • Position 2 shows the transition area between the first expansion section 60a, 60b and the second expansion section 66a, 66b.
  • Position 3 shows a position in which the respective second expansion sections 60a, 60b are fluidly connected to the fluid inlet 23a and the fluid outlet 23b.
  • Position 4 shows a main flow position in which the control passage is fully connected to fluid inlet 23a and fluid outlet 23b.
  • the valve device 10 has a constant opening cross section over the entire angular range 64 in the first valve position (Pos. 1), which is the minimum flow position 51. If the valve device is in the second valve position (pos. 2), the flow cross section changes from the first, constant flow cross section of the first expansion section 60a, 60b to the second expansion section 66a, 66b with its continuously increasing opening cross section. In the third valve position (pos. 3), the second expansion sections 60a, 60b are fluidically connected to the fluid inlet 23a and the fluid outlet 23b. When sweeping the circumferential angle 65 of the second expansion section 66a, 66b, the opening cross section increases continuously to.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Lift Valve (AREA)
  • Valve Housings (AREA)

Abstract

L'invention concerne un dispositif de soupape (10), en particulier un détendeur, servant à réguler un écoulement d'un fluide, en particulier pour un circuit de fluide frigorigène dans un véhicule. Ledit dispositif de soupape (10) comprend un carter d'élément de soupape (12) et un élément de soupape (14) à l'intérieur du carter d'élément de soupape (12), l'élément de soupape (14) ayant un trou d'écoulement de commande (30) et au moins une découpe d'expansion (40a, 40b). Selon l'invention, la découpe d'expansion (40a, 40b) comprend une première partie d'expansion (60a, 60b) qui présente une section transversale d'écoulement sensiblement constante le long de la direction d'écoulement.
EP21820252.1A 2020-12-01 2021-12-01 Dispositif de soupape Withdrawn EP4256253A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102020215165 2020-12-01
DE102021213523.4A DE102021213523A1 (de) 2020-12-01 2021-11-30 Ventilvorrichtung
PCT/EP2021/083756 WO2022117641A1 (fr) 2020-12-01 2021-12-01 Dispositif de soupape

Publications (1)

Publication Number Publication Date
EP4256253A1 true EP4256253A1 (fr) 2023-10-11

Family

ID=78822627

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21820252.1A Withdrawn EP4256253A1 (fr) 2020-12-01 2021-12-01 Dispositif de soupape

Country Status (2)

Country Link
EP (1) EP4256253A1 (fr)
WO (1) WO2022117641A1 (fr)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1601103A (en) * 1977-03-11 1981-10-28 Concentric Controls Ltd Gas taps
JP3552438B2 (ja) * 1996-02-05 2004-08-11 株式会社デンソー 流量制御装置
DE102017208181A1 (de) 2017-03-07 2018-09-13 Robert Bosch Gmbh Ventil zur Steuerung eines Fluidstroms

Also Published As

Publication number Publication date
WO2022117641A1 (fr) 2022-06-09

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