WO2024078720A1 - Soupape de détente - Google Patents

Soupape de détente Download PDF

Info

Publication number
WO2024078720A1
WO2024078720A1 PCT/EP2022/078516 EP2022078516W WO2024078720A1 WO 2024078720 A1 WO2024078720 A1 WO 2024078720A1 EP 2022078516 W EP2022078516 W EP 2022078516W WO 2024078720 A1 WO2024078720 A1 WO 2024078720A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow
section
control body
expansion valve
flow channel
Prior art date
Application number
PCT/EP2022/078516
Other languages
German (de)
English (en)
Inventor
Hans-Carsten GÖTTSCHE-GÖTZE
Timon JANSEN
Jean KÜBBELER
Robert Sabic
Herbert SCHÖNHOFEN
Original Assignee
Pierburg 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 Pierburg Gmbh filed Critical Pierburg Gmbh
Priority to PCT/EP2022/078516 priority Critical patent/WO2024078720A1/fr
Publication of WO2024078720A1 publication Critical patent/WO2024078720A1/fr

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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/04—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the invention relates to an expansion valve with a flow housing with an inlet and an outlet, an actuator, via which a control body is axially movable, a flow channel which is arranged fluidically between the inlet and the outlet, wherein the flow channel has a first flow section with at least one evaporation cross-section which can be opened or closed by means of a first control body section, and a second flow section in which a flow gap is formed between a second control body section and a correspondingly designed flow channel inner wall, wherein a flow deflection structure is arranged in the second flow section, which is fluidically arranged between the inlet and the evaporation cross-section.
  • the disclosed expansion valve comprises a control body with a first control body section, through which an evaporation cross-section can be opened or closed, wherein the control body has circumferential grooves in a second control body section, in particular a spiral groove, through which a second flow cross-section is formed in the open state of the expansion valve, at which a throttling of the fluid flowing past takes place.
  • the fluid initially flows through the relatively narrow evaporation cross-section and then through the second flow cross-section, the size of which can be varied by moving the grooves in relation to a flow edge in the flow channel inner wall.
  • Another exemplary expansion valve is disclosed in JP 2015-143543 A.
  • both the control body and the inner wall of the flow channel have circumferential grooves in which the fluid flowing past is swirled, thereby forming a turbulent flow boundary layer that ensures that the fluid flows past with relatively little noise and wear, particularly at the transitions between two surfaces at an angle to one another.
  • the invention is therefore based on the object of creating an expansion valve in which a significant turbulence of the flow occurs, in particular at the time of opening.
  • the expansion valve according to the invention has a flow housing with an inlet and an outlet, through which a fluid, in particular a coolant, flows from the inlet to the outlet.
  • the expansion valve also has a control body which can be moved in the axial direction in a stroke-like manner, wherein the movement of the control body can be generated, for example, by an actuator.
  • the expansion valve also has a flow channel which is preferably formed by the flow housing and is arranged fluidically between the inlet and the outlet, whereby the flow channel fluidically connects the inlet and the outlet.
  • the flow channel has a first
  • Control body section and a first
  • Flow channel inner wall section at least one
  • the flow channel inner wall section encloses the correspondingly designed first control body section along the circumference, whereby an axially extending
  • Evaporation gap can be formed, wherein the evaporation cross section is preferably the narrowest cross section of the evaporation gap in which the fluid relaxes and thus expands, whereby at least a part of the fluid flowing through the evaporation cross section changes its state of aggregation from liquid to gaseous, i.e. evaporates.
  • the flow channel further comprises a second flow section in which a flow gap is formed between a second control body section formed by a second subsection of the control body and the correspondingly formed flow channel inner wall, or a flow channel inner wall section that serves as a valve seat, when the second control body section is lifted off the valve seat, which preferably has an annular cross section that is larger than the evaporation cross section.
  • a flow deflection structure is arranged in the second flow section, which is arranged fluidically between the inlet and the evaporation cross section. Consequently, the fluid flows before it flows through the evaporation cross-section, through the flow deflection structure, whereby the fluid flow is deflected and thus slowed down.
  • the flow gap in which the flow deflection structure is arranged is closed when the expansion valve is closed, i.e. when the control body completely closes the flow channel, by the second control body section resting on the inner wall of the flow channel.
  • either the flow deflection structure itself or a surface adjacent to the flow deflection structure in the second flow section rests on the valve seat.
  • a surface of the control body adjacent to the flow deflection structure could rest on a corresponding surface on the inner wall of the flow channel and thereby close the flow gap.
  • the expansion valve When the expansion valve is opened, i.e. when the control body is moved in the axial direction, the flow gap in the second flow section is released, whereby the fluid flows through the flow channel and the evaporation cross section. Due to the low temperatures of a fluid used in a refrigeration circuit, a relatively high pressure suddenly forms in a conventional expansion valve, especially during the opening process of the expansion valve in front of the evaporation cross section. In the expansion valve according to the invention, the fluid flows shortly after opening, starting from the inlet, initially along the second flow section and passes the flow deflection structure.
  • the flow deflection structure causes a deflection of at least part of the fluid flow, which affects the entire flow, whereby the entire fluid flow is already diverted by means of the flow deflection structure before the actual throttle point at the evaporation cross section. is throttled or slowed down.
  • the pressure of the fluid in the flow gap is reduced before it reaches the evaporation cross-section, which means that the flow rate through the evaporation cross-section can be regulated much more precisely.
  • the flow deflection structure is arranged in such a way that, starting from a defined control body stroke, the flow deflection structure is positioned completely outside the second flow channel inner wall section in relation to the stroke direction.
  • this defined control body stroke is exceeded, the distance between the second flow channel inner wall section and the control body becomes smaller than the distance between the second flow channel inner wall section and the flow deflection structure, so that the latter is no longer within the narrowest cross-section and therefore no longer has a relevant influence on the flow. Accordingly, no more turbulence is generated in the flow gap, but rather there is a largely straight-line flow through the flow gap without additional pressure losses.
  • the flow deflection structure therefore only has a significant effect on the fluid flow shortly after the expansion valve opens when the flow gap is relatively small.
  • the flow deflection structure is formed by at least one circumferential recess in the control body and/or the flow channel inner wall.
  • the circumferential recess is preferably a triangular groove-like depression either in the control body or in the flow channel inner wall, whereby alternatively both the control body and the flow channel inner wall can each have a circumferential recess.
  • the circumferential recess causes a widening of the flow gap in the flow direction and a In relation to the widening, the flow gap is narrowed, whereby at least a partial flow of the fluid flowing through the flow gap flows into the recess and is thereby slightly diverted in relation to the main flow direction along the flow gap at the inlet edge of the recess, where the flow gap begins to widen.
  • the flow gap begins to widen.
  • the outlet edge arranged at the fluidic end of the recess, there is another slight diversion. This multiple diversion of the flow creates turbulence, which throttles or slows down the flow and thus reduces the pressure.
  • the surface opposite the recess can have a corresponding raised structure which projects into the recess at least when the valve is closed and slightly open, whereby a labyrinth-like gap is formed in the region of the flow deflection structure, which causes a deflection of the entire flow.
  • a first circumferential recess and a second circumferential recess are formed in the control body.
  • the flow deflection structure thus has two recesses, whereby the number of flow deflections is doubled. Furthermore, the recesses in the control body can be produced more easily than in the flow housing, so that the additional manufacturing costs for the recesses are relatively low.
  • the recess has a V-shaped cross-section, whereby a relatively acute angle is formed at the base of the recess, which causes a relatively strong flow deflection.
  • the V-shaped cross-section forms preferably an isosceles triangle whose line of symmetry is arranged perpendicular to the lateral surface of the control body, whereby the deflection angles at the leading edge and the trailing edge of the recess are equal.
  • the two recesses are arranged adjacent to one another in relation to the flow direction, thereby forming a stepped structure.
  • the first recess is thus arranged upstream of the second recess, so that the exit edge of the first recess forms the entry edge of the second recess.
  • the flow is deflected relatively strongly at this edge, so that with the respective deflections at the base of each recess, three relatively strong deflections of the flow occur, each of approximately 90°, whereby the pre-throttling effect is significantly stronger than with just one recess.
  • closed circumferential chambers are formed by the two recesses when the expansion valve is closed.
  • the circumferential chambers are formed by the flow deflection structure being completely in contact with the opposite corresponding surface, whereby the circumferential recesses are completely closed by the contacting surface. This is particularly advantageous when the flow deflection structure is arranged at the beginning of the flow gap from a fluidic point of view.
  • At least a partial section of the second control body section in the second flow section is convex, wherein the second control body section in the region of the flow deflection structure does not have to be convex, but only has a
  • the surface adjacent to the flow deflection structure can be convex and, for example, when the expansion valve is closed, lies sealingly against the corresponding flow channel inner wall so that the expansion valve is closed.
  • the control body in the second control body section is not completely conical.
  • the contour of the entire second control body section is designed such that a conical surface enclosing the second control body section touches the second control body section at least two points closest to the flow channel inner wall, namely the point on the convex partial section closest to the second flow channel inner wall section and the point on the flow deflection structure closest to the second flow channel inner wall section, the conicity of the enclosing surface corresponding to the conicity of the second flow channel inner wall section forming the valve seat. Due to the convex contact surface, the second control body section only touches the preferably conical flow channel inner wall along one line, which ensures a relatively high level of tightness of the expansion valve in the closed state. In this case, in the area of the flow deflection structure, the control body should advantageously not rest against the inner wall of the flow channel.
  • the flow deflection structure has a sharp edge at at least one deflection point.
  • a sharp-edged flow deflection structure causes flow separation, which can cause relatively strong turbulence in the flow and thus result in a pressure loss, which further reduces the pressure of the fluid.
  • the flow channel in the first flow section is cylindrical, wherein the first control body section is also cylindrical in a corresponding manner.
  • this first flow section in which the evaporation cross section is also formed, an evaporation gap with a constant evaporation cross section is formed by the two cylindrical surfaces of the control body and the flow channel in the closed and slightly open state of the expansion valve. Consequently, the evaporation cross section remains constant shortly after the expansion valve opens for a certain stroke length, which is preferably 5% to 20% of the control body stroke, which corresponds approximately to the stroke length within which the flow deflection structure exerts a significant influence on the flow in the second flow section.
  • the flow deflection structure extends over at least 30% of the length of the second control body section.
  • the length of the second control body section essentially corresponds to the length of the second flow section.
  • control body and the flow channel in the second flow section are essentially conical, with the conicity of the control body essentially corresponding to the conicity of the flow channel. Consequently, the second control body section lies flat on the second flow channel inner wall section and thereby closes the flow gap in the second flow section.
  • the conicity means that with increasing stroke of the control body, the flow cross section of the The flow gap in the second flow section increases continuously, allowing the flow rate to be regulated. Furthermore, the angle of the cone determines how many millimeters of flow gap are opened or closed per millimeter of control body stroke.
  • a conical third control body section is connected downstream of the first control body section, whereby the evaporation cross section is increased proportionally with increasing valve stroke by increasing the distance between the conical control body surface and the flow channel inner wall, whereby the flow channel inner wall itself can be cylindrical or conical.
  • a convex fourth control body section follows downstream of the conical third control body section, i.e., with respect to the flow direction, a spherical control body section follows after the conical third control body section, which increases the evaporation cross section in an integral manner with increasing valve stroke, whereby the flow rate of the fluid increases disproportionately with increasing valve stroke.
  • Figure 1 is a partial view of the flow housing of the expansion valve in the closed state in a sectional view, the section running through the control body axis,
  • FIG 2 is an enlarged detailed view of the flow channel of the expansion valve shown in Figure 1 in the slightly opened state
  • Figure 3 is an enlarged detailed view of the flow deflection structure of the flow channel shown in Figure 2.
  • Fig. 1 shows a section of an expansion valve 10 for the refrigeration circuit of a battery-electric vehicle in the closed state.
  • the expansion valve 10 has a flow housing 12 with a cylindrical inlet 14 and a conical outlet 16.
  • the expansion valve 10 also has a control body 20 which is arranged to be axially movable in a corresponding opening 121 of the flow housing 12.
  • the control body 20 can be moved, for example, by means of an actuator and carries out a control body stroke h.
  • a flow channel 30 with a flow channel inner wall 124 is formed in the flow housing 12, the flow channel 30 having a plurality of differently shaped sections and extending between the inlet 14 and the outlet 16.
  • FIG. 2 shows a detailed view of the expansion valve 10 according to the invention in a slightly opened state, with the control body 20 being raised by a stroke hl of approximately 10% of the total control body stroke h.
  • Figure 2 shows in particular the flow channel 30 with a first Flow section 301 and a second flow section 302.
  • an evaporation gap 21 is arranged, which is formed between a cylindrical first control body section 201 and a hollow cylindrical flow channel inner wall section 125.
  • An evaporation cross section 24 is also formed by an evaporation edge 240 arranged at the upstream end of the first flow section 301 and the control body 20, which represents the narrowest cross section of the flow channel 30, wherein the liquid coolant flowing through the flow channel 30 is expanded when flowing through the evaporation cross section 24 and is thereby evaporated.
  • the cylindrical first control body section 201 and the cylindrical flow channel inner wall section 125 thus form an evaporation gap 21 with a constant cross-section, whereby the evaporation cross-section 24 is constant over a stroke that corresponds approximately to the axial length of the cylindrical first control body section 201.
  • the cylindrical first flow section 301 and the cylindrical first control body section 201 extend in the axial direction over approximately 10% of the control body stroke h.
  • a third conical control body section 203 Downstream of the first control body section 201 there is a third conical control body section 203 which tapers in the downstream direction, whereby the evaporation cross section 24, when the third control body section 203 is at the level of the evaporation edge 240 with respect to the stroke direction of the control body 20, is increased proportionally with increasing stroke, whereby the flow rate flowing through the evaporation cross section 24 can be increased.
  • a fourth convex control body section 204 Downstream of the third conical control body section 203 there is a fourth convex control body section 204, as shown in Fig. 1, which, when it is at the level of the evaporation cross section 24 with respect to the stroke direction of the control body 20, becomes a disproportionate enlargement of the evaporation cross section 24 and thus to a disproportionate increase in the flow rate.
  • a second flow section 302 is arranged upstream of the first flow section 301.
  • the flow housing 12 has a conically shaped flow channel inner wall 124 with an opening angle in relation to the control body axis R of approximately 45°.
  • a second control body section 202 is essentially conically formed in a corresponding manner, so that the second control body section 202 and the flow channel inner wall 124 form a flow gap 22 which extends in the flow direction in the open state of the expansion valve 10 from the inlet 14 to the evaporation cross section 24.
  • a flow deflection structure 40 is arranged, which extends over 40% of the length L of the first control body section 201 and is formed by two circumferential recesses 43, 46 adjacent to one another in relation to the flow direction, wherein the flow deflection structure is arranged in terms of flow between the inlet 14 and the evaporation cross section 24.
  • Each recess 43, 46 has a V-shaped cross section with an angle of 90°, so that due to the inclination of the surface of the first control body section 202 of approximately 45° in relation to the control body axis R, a step structure 210 made up of two successive cylindrical sections 211, 212 of different diameters is formed by the two recesses 43, 46.
  • the second control body section Downstream of the flow deflection structure 40, i.e. between the flow deflection structure 40 and the first control body section 201, the second control body section is convex and consequently has a spherically shaped section which, in the closed state, rests on the flow channel inner wall 124 in the second flow section 302. rests, whereby the control body 20 closes the flow channel 30, as shown in Fig. 1.
  • the flow deflection structure 40 with the two recesses 43, 46 rests on the flow channel inner wall 124 in the closed state, so that the recesses 43, 46 are closed and therefore form circumferential chambers 431, 461.
  • the points of the flow deflection structure 40 and the convex partial section 205 closest to the second flow channel inner wall section 124 lie on a line M which corresponds in terms of flatness and angle to the contour of the second flow channel inner wall section 124.
  • the flow deflection structure 40 causes a deflection and turbulence of the refrigerant flow K flowing through the flow gap 22.
  • Refrigerant flow K flows through the inlet 14 into the flow gap 22 and passes the flow deflection structure 40.
  • a first slight deflection of the refrigerant flow K flowing directly past the inlet edge 41 takes place, with the sharp inlet edge 41 causing flow separations that cause turbulence in the flow.
  • the refrigerant flows in the direction of a base 44 of the first recess 43, at which a relatively strong deflection of the refrigerant flow K by approximately 90° takes place, whereupon the refrigerant flows in the direction of the intermediate edge 42 designed as a sharp edge 45, which forms the outlet edge of the first recess 43 and also the inlet edge of the second recess 46.
  • the intermediate edge 42 the coolant flow K is again deflected relatively strongly by approximately 90°, whereby the deflection and the flow separation caused by the sharp edge 42 cause strong turbulences, which continue from the flow deflection structure into the gap.
  • the coolant flows Refrigerant to a base 48 of the second recess 46, where a third relatively strong deflection of approximately 90° takes place.
  • the refrigerant then flows in the direction of the outlet edge 47 of the second recess 46, where a further slight deflection of the refrigerant flow K takes place.
  • the refrigerant flow K is thus diverted three times relatively strongly, creating a pre-throttling effect that leads to a first pressure reduction before the refrigerant flow K reaches the evaporation cross-section 24, where the actual throttling and thus the evaporation of the refrigerant flow K takes place.
  • the pre-throttling effect of the flow diverting structure 40 decreases due to the ever-increasing flow cross-section in the flow gap 22.
  • the narrowest flow gap 22 is located outside the flow diverting structure 40, whereby its influence on the flow in the flow gap 22 is almost completely eliminated, since the flow diverting structure 40 is arranged in an area through which the flow is significantly lower and in which there is therefore a lower flow velocity.
  • the turbulences T caused by the recesses 43, 46 have no significant influence on the cold flow K as soon as the distance b between the second control body section 202 and the second flow channel inner wall section 124 becomes smaller than the distance of the recesses 43, 46 to the second
  • Flow channel inner wall section 124 whereby the cold flow K forms a laminar flow, so that when the expansion valve 10 is fully open, no significant effect emanates from the flow deflection structure 40.
  • the high pressure that prevails as a result of the low temperatures of the coolant when the expansion valve 10 is opened can be reduced relatively significantly by the turbulence T in the recesses 43, 46 caused by the flow deflection structure 40, so that the pressure of the cold flow K in front of the evaporation cross section 24 is significantly reduced.
  • the control effort is reduced because the flow rate through the evaporation cross section 24 can be regulated much more precisely.
  • wear is reduced because significantly less harmful cavitation can occur in the flow channel 30.

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

Abstract

L'invention concerne une soupape de détente (10) comprenant un boîtier d'écoulement (12) doté d'une entrée (14) et d'une sortie (16), un corps de commande (20) axialement mobile et un canal d'écoulement (30) qui est placé en termes d'écoulement entre l'entrée (14) et la sortie (16), le canal d'écoulement (30) ayant une première partie d'écoulement (301) dans laquelle au moins une section transversale d'évaporation (24) est formée entre une première partie corps de commande (201) et une première partie paroi interne de canal d'écoulement (125), et ayant une seconde partie d'écoulement (302) dans laquelle un espace d'écoulement (22) est formé entre une seconde partie corps de commande (202) et une paroi interne de canal d'écoulement formée de manière correspondante (124), une structure de déviation d'écoulement (40) qui est agencée en termes d'écoulement entre l'entrée (14) et la section transversale d'évaporation (22) étant placée dans la seconde partie d'écoulement (302), l'espace d'écoulement dans lequel la structure de déviation d'écoulement (40) est agencée étant fermé dans un état fermé de la soupape de détente (10) par le support de la seconde partie corps de commande (202) sur la paroi interne de canal d'écoulement (124). La structure de déviation d'écoulement (40) provoque une constriction préliminaire du fluide avant qu'il n'atteigne la section transversale d'évaporation (24), ce qui permet de réduire la pression en amont de la section transversale d'évaporation (24).
PCT/EP2022/078516 2022-10-13 2022-10-13 Soupape de détente WO2024078720A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/EP2022/078516 WO2024078720A1 (fr) 2022-10-13 2022-10-13 Soupape de détente

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2022/078516 WO2024078720A1 (fr) 2022-10-13 2022-10-13 Soupape de détente

Publications (1)

Publication Number Publication Date
WO2024078720A1 true WO2024078720A1 (fr) 2024-04-18

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ID=84330513

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2022/078516 WO2024078720A1 (fr) 2022-10-13 2022-10-13 Soupape de détente

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4044991A (en) * 1975-10-06 1977-08-30 Consolidated Controls Corporation High energy loss fluid flow control device
JP2005069644A (ja) * 2003-08-27 2005-03-17 Daikin Ind Ltd 多段電動膨張弁及び冷凍装置
WO2006093149A1 (fr) 2005-02-28 2006-09-08 Daikin Industries, Ltd. Soupape de dilatation et dispositif de refrigeration
JP2015143543A (ja) 2014-01-31 2015-08-06 株式会社鷺宮製作所 制御弁
JP2021067314A (ja) * 2019-10-23 2021-04-30 株式会社鷺宮製作所 電動弁及び冷凍サイクルシステム

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4044991A (en) * 1975-10-06 1977-08-30 Consolidated Controls Corporation High energy loss fluid flow control device
JP2005069644A (ja) * 2003-08-27 2005-03-17 Daikin Ind Ltd 多段電動膨張弁及び冷凍装置
WO2006093149A1 (fr) 2005-02-28 2006-09-08 Daikin Industries, Ltd. Soupape de dilatation et dispositif de refrigeration
JP2015143543A (ja) 2014-01-31 2015-08-06 株式会社鷺宮製作所 制御弁
JP2021067314A (ja) * 2019-10-23 2021-04-30 株式会社鷺宮製作所 電動弁及び冷凍サイクルシステム

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