EP2620724B1 - Détendeur - Google Patents

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Publication number
EP2620724B1
EP2620724B1 EP11826895.2A EP11826895A EP2620724B1 EP 2620724 B1 EP2620724 B1 EP 2620724B1 EP 11826895 A EP11826895 A EP 11826895A EP 2620724 B1 EP2620724 B1 EP 2620724B1
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EP
European Patent Office
Prior art keywords
orifice
refrigerant
outflow
expansion valve
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.)
Active
Application number
EP11826895.2A
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German (de)
English (en)
Other versions
EP2620724A4 (fr
EP2620724A1 (fr
Inventor
Yoshimasa Kikuchi
Shigetaka Wakisaka
Takashi Shimamura
Keiji Tomioka
Motohiko Fukuoka
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP2620724A1 publication Critical patent/EP2620724A1/fr
Publication of EP2620724A4 publication Critical patent/EP2620724A4/fr
Application granted granted Critical
Publication of EP2620724B1 publication Critical patent/EP2620724B1/fr
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the present invention relates to an expansion valve, and particularly relates to an expansion valve which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant.
  • expansion valves such as the one disclosed in Patent Literature 1 (Japanese Laid-open Patent Application No. 2009-228689 ).
  • This expansion valve is provided to a refrigerant circuit of a refrigeration apparatus and is used to depressurize a liquid refrigerant, and as shown in FIG. 5 , the expansion valve has primarily a valve main body 10, a valve body 20, and a drive mechanism 30.
  • the valve main body 10 is a member in which a valve seat 12 opening into a valve chest 11 is formed.
  • Formed in the valve main body 10 are a refrigerant inlet 13 where refrigerant flows in from the side of the valve chest 11, and a refrigerant outlet 14 where refrigerant flows out underneath the valve chest 11.
  • a refrigerant inflow tube 40 is connected to the refrigerant inlet 13, and a refrigerant outflow tube 50 is connected to the refrigerant outlet 14.
  • the valve body 20 is a member that is caused to reciprocate relative to the valve seat 12 by the drive mechanism 30.
  • the drive mechanism 30 is composed of a motor, a solenoid, or the like. With such a configuration, the flow rate of liquid refrigerant passing between the refrigerant inflow tube 40 and the refrigerant outflow tube 50 is adjusted while the refrigerant is depressurized. Further expansion valves are disclosed in JP 2007/292336 A , JP 2004/340260A , JP H09/42510 A , JP 2004/132498 or EP 2211077 A2
  • an orifice 80 is formed in the valve seat 12 as shown in FIG. 6 .
  • This orifice 80 is composed only of a portion 81 which has the same diameter (a diameter D0) along the direction of refrigerant outflow (specifically, downward along the reciprocating direction axis line X of the valve body 20).
  • An object of the present invention is to minimize the noise that occurs under conditions such that the refrigerant passes through the refrigerant inlet in a liquid single phase and through the refrigerant outlet also in a liquid single phase, in an expansion valve which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant.
  • An expansion valve according to the invention is an expansion valve which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant, the expansion valve comprising a valve main body in which a valve seat opening into a valve chest is formed, and a valve body which reciprocates relative to the valve chest.
  • An orifice formed in the valve seat has an orifice entrance having the smallest diameter, an orifice middle section which widens in diameter along the direction of refrigerant outflow from the orifice entrance so as to form a first taper angle, and an orifice exit which either widens in diameter or does not change in diameter along the direction of refrigerant outflow from the orifice middle section so as to form a second taper angle smaller than the first taper angle, wherein a second outflow direction length of the orifice exit along the direction of refrigerant outflow is equal to or less than the first outflow direction length of the orifice middle section along the direction of refrigerant outflow.
  • the inventors of the present application have discovered that when the expansion valve is used under conditions such that the refrigerant passes through the refrigerant inlet in a liquid single phase and through the refrigerant outlet also in a liquid single phase, noise is caused by sounds from cavitation when the refrigerant passes through the orifice and resonance sounds in the refrigerant outflow tube after the refrigerant passes through the orifice.
  • the conventional expansion valve when the refrigerant passes through the orifice, separation of the refrigerant flow occurs immediately after the refrigerant has flowed from the valve chest, which has a large flow passage cross section, to the orifice, which has a small flow passage cross section.
  • the inventors of the present application have conducted thoroughgoing experiments towards designing a shape of the orifice that would address such noise.
  • the inventors of the present application have discovered that the noise described above can be minimized if the orifice has an orifice entrance having the smallest diameter, an orifice middle section which widens in diameter along the direction of refrigerant outflow from the orifice entrance so as to form a first taper angle, and an orifice exit which either widens in diameter or does not change in diameter along the direction of refrigerant outflow from the orifice middle section so as to form a second taper angle smaller than the first taper angle.
  • the refrigerant flowing into the orifice from the valve chest first flows into the orifice entrance of the orifice, similar to the conventional example, immediately after which flow separation occurs, and local drops in pressure are likely to occur due to this separation.
  • the pressure of the refrigerant can be recovered immediately after it has flowed into the orifice entrance. Such pressure recovery minimizes the occurrence of cavitation, and as a result minimizes the sounds caused by cavitation when the refrigerant passes through the orifice.
  • the separated refrigerant can re-agglutinate because of the formation of the orifice exit wherein the diameter widens or the diameter does not change from the orifice middle section along the direction of refrigerant outflow so as to form a second taper angle which is smaller than the first taper angle.
  • Such re-agglutination of the refrigerant minimizes the occurrences of spurting which causes pressure fluctuation, and as a result, resonance sound in the refrigerant outflow tube is minimized.
  • the expansion valve employing the shape of the orifice having the orifice entrance, the orifice middle section, and the orifice exit as described above makes it possible to minimize noises occurring when the expansion valve is used in conditions such that the refrigerant passes through the refrigerant inlet in a liquid single phase and through the refrigerant outlet also in a liquid single phase.
  • the orifice exit can be prevented from becoming too long, and increases in pressure loss in the orifice exit can be prevented.
  • An expansion valve according to a first preferred embodiment is the expansion valve according to the invention, characterized in that a first outflow direction length of the orifice middle section along the direction of refrigerant outflow is one or more times the minimum diameter of the orifice entrance.
  • An expansion valve according to a second preferred embodiment is the expansion valve according to the invention or the first preferred embodiment, characterized in that the first taper angle is 10 degrees or greater and 60 degrees or less.
  • the first taper angle is 10 degrees or greater, the effect of pressure recovery immediately after the refrigerant has flowed into the orifice entrance can be reliably achieved. Moreover, because the first taper angle is 60 degrees or less, it is also possible for the refrigerant in the orifice middle section to re-agglutinate. Specifically, in this expansion valve, having the first taper angle in the angle range described above makes both pressure recovery and refrigerant re-agglutination possible.
  • An expansion valve according to a third preferred embodiment is the expansion valve according to any of the invention or the first or second preferred embodiments, characterized in that a second inclination angle formed by the orifice exit with a plane orthogonal to the direction of refrigerant outflow is greater than a first inclination angle formed by the orifice middle section with a plane orthogonal to the direction of refrigerant outflow, and is 90 degrees or less.
  • the diameter can be prevented from narrowing along the direction of refrigerant outflow.
  • the refrigerant flow can thereby be prevented from contracting in the orifice exit, and the effect of minimizing pressure fluctuation in the orifice exit can be improved.
  • FIG. 1 is a schematic cross-sectional view of an expansion valve 1 according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view showing a valve seat of an expansion valve according to an embodiment of the present invention.
  • Components in FIGS. 1 and 2 that are similar to those of FIGS. 5 and 6 showing a conventional example (specifically, components other than the orifice 80) are denoted by the same symbols.
  • the expansion valve 1 is an expansion valve which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant, and the expansion valve has primarily a valve main body 10, a valve body 20, and a drive mechanism 30.
  • the valve main body 10 is a member in which a valve seat 12 opening into a valve chest 11 is formed.
  • Formed in the valve main body 10 are a refrigerant inlet 13 where refrigerant flows in from the side of the valve chest 11, and a refrigerant outlet 14 where refrigerant flows out underneath the valve chest 11.
  • a refrigerant inflow tube 40 is connected to the refrigerant inlet 13, and a refrigerant outflow tube 50 is connected to the refrigerant outlet 14.
  • the valve body 20 is a member that is reciprocated relative to the valve seat 12 by the drive mechanism 30.
  • the drive mechanism 30 is composed of a motor, a solenoid, or the like. Such a configuration is designed so that the flow rate of liquid refrigerant passing between the refrigerant inflow tube 40 and the refrigerant outflow tube 50 is adjusted while the refrigerant is depressurized.
  • the expansion valve 1 is used in conditions such that the refrigerant passes through the refrigerant inlet 13 in a liquid single phase and through the refrigerant outlet 14 also in a liquid single phase.
  • an orifice 60 is formed in the valve seat 12.
  • the orifice 60 has an orifice entrance 61, an orifice middle section 62, and an orifice exit 63.
  • the orifice entrance 61 which faces the valve chest 11, is the portion having the smallest diameter.
  • the orifice entrance 61 is a cylindrical portion having the same diameter (a minimum diameter D0) along the direction of refrigerant outflow (specifically, downward along a reciprocating direction axis line X of the valve body 20). Denoting the length of the orifice entrance 61 in the refrigerant outflow direction as the entrance length L0, the entrance length L0 is much smaller than the minimum diameter D0, and in this case is 0.3 times or less the length of the minimum diameter D0.
  • valve body 20 By coming in contact with the orifice entrance 61, the valve body 20 blocks the flow of refrigerant between the refrigerant inlet 13 and the refrigerant outlet 14, and by separating from the orifice entrance 61, the valve body 20 allows refrigerant to flow between the refrigerant inlet 13 and the refrigerant outlet 14.
  • the orifice middle section 62 is a cylindrical portion which widens in diameter from the orifice entrance 61 toward the direction of refrigerant outflow so that a first taper angle ⁇ is created. Denoting the length of the orifice middle section 62 along the direction of refrigerant outflow as the first outflow direction length L1, the first outflow direction length L1 is one or more times the minimum diameter D0.
  • the first taper angle ⁇ is an angle 10 degrees or greater and 60 degrees or less.
  • the inclination angle formed by the orifice middle section 62 with a plane orthogonal to the direction of refrigerant outflow (the angle on the side forming an acute angle in this case) is a first inclination angle ⁇ .
  • the orifice exit 63 is a cylindrical portion wherein the diameter widens or the diameter does not change from the orifice middle section 62 along the direction of refrigerant outflow, so as to form a second taper angle ⁇ which is smaller than the first taper angle ⁇ .
  • the second outflow direction length L2 Denoting the length of the orifice exit 63 along the direction of refrigerant outflow as the second outflow direction length L2, the second outflow direction length L2 is equal to or less than the first outflow direction length L1.
  • the second outflow direction length L2 is also equal to or greater than 0.3 times the minimum diameter D0.
  • the second inclination angle ⁇ is greater than the first inclination angle ⁇ and is equal to or less than 90 degrees.
  • the separated refrigerant can re-agglutinate because of the formation of the orifice exit 63 wherein the diameter widens or the diameter does not change from the orifice middle section 62 along the direction of refrigerant outflow so as to form a second taper angle ⁇ which is smaller than the first taper angle ⁇ .
  • Such re-agglutination of the refrigerant minimizes the occurrences of spurting which causes pressure fluctuation, and as a result, resonance sound in the refrigerant outflow tube 50 is minimized.
  • the expansion valve 1 employing the shape of the orifice 60 having the orifice entrance 61, the orifice middle section 62, and the orifice exit 63 as described above makes it possible to minimize noises occurring when the expansion valve is used in conditions such that the refrigerant passes through the refrigerant inlet 13 in a liquid single phase and through the refrigerant outlet 14 also in a liquid single phase.
  • the first outflow direction length L1 of the orifice middle section 62 along the direction of refrigerant outflow is one or more times the minimum diameter D0 of the orifice entrance 61
  • refrigerant can re-agglutinate not only in the orifice exit 63 but in the orifice middle section 62 as well, whereby the effect of minimizing resonance sounds in the refrigerant outflow tube 50 can be improved.
  • the second outflow direction length L2 of the orifice exit 63 along the direction of refrigerant outflow is equal to or greater than 0.3 times the minimum diameter D0 of the orifice entrance 61, the effect of minimizing resonance sounds in the refrigerant outflow tube 50 can be reliably achieved.
  • the expansion valve 1 because the first taper angle ⁇ is 10 degrees or greater, the effect of pressure recovery immediately after the refrigerant has flowed into the orifice entrance 61 can be reliably achieved. Moreover, because the first taper angle ⁇ is 60 degrees or less, it is also possible for the refrigerant in the orifice middle section 62 to re-agglutinate. Specifically, in the expansion valve 1, having the first taper angle ⁇ in the angle range described above makes both pressure recovery and refrigerant re-agglutination possible.
  • the second inclination angle ⁇ formed by the orifice exit 63 with a plane orthogonal to the direction of refrigerant outflow is 90 degrees or less, the diameter can be prevented from narrowing along the direction of refrigerant outflow.
  • the refrigerant flow can thereby be prevented from contracting in the orifice exit 63, and the effect of minimizing pressure fluctuation in the orifice exit 63 can be improved.
  • the orifice exit 63 can be prevented from becoming too long, and increases in pressure loss in the orifice exit 63 can be prevented.
  • FIG. 3 is a graph showing the relationship between cavitation number and noise value according to differences in the shape of the orifice formed in the valve seat 12.
  • FIG. 4 is a cross-sectional view showing the valve seat 12 of an expansion valve according to a comparative example.
  • the minimum diameter D0 was set to 1.6 mm, the entrance length L0 to 0.5 mm, the first taper angle ⁇ to 20 degrees (the first inclination angle ⁇ to 80 degrees), the first outflow direction length L1 to 3.8 mm, the second taper angle ⁇ to 0 degrees (the second inclination angle ⁇ to 90 degrees), and the second outflow direction length L2 to 0.7 mm.
  • R410A was used as the refrigerant
  • the depressurization width between the refrigerant inlet 13 and the refrigerant outlet 14 was 0.8 MPa
  • the refrigerant flow rate was 75 to 85 kg/h
  • the cavitation number ⁇ (based on the refrigerant outlet 14) was varied between approximately -0.1 to approximately 0.9 by varying the refrigerant temperature between 5°C to 25°C
  • the noise value (the noise value caused by cavitation) in the expansion valve 1 alone at a distance of 0.3 m was measured (refer to the value of the working example in FIG. 3 ). Measurement of resonance sounds was also taken separately while the refrigerant outflow tube 50 was connected.
  • the noise value caused by cavitation is minimized to 55 dBA or less in conditions such that the refrigerant passes through the refrigerant inlet 13 in a liquid single phase and through the refrigerant outlet 14 also in a liquid single phase (in other words, conditions such that the cavitation number ⁇ is 0 or greater).
  • the working example of the orifice 60 there was no resonance in the refrigerant outflow tube 50, and noise from resonance sounds was at a level that could be ignored.
  • the noise level caused by cavitation increased to a maximum of 65 dBA under the same measurement conditions as the working example, and the noise level caused by cavitation had increased by about 10 dBA above that of the working example of the orifice 60 described above (refer to the value of the conventional example in FIG. 3 ).
  • the orifice 80 of the conventional example similar to the working example of the orifice 60, there was no resonance in the refrigerant outflow tube 50, and noise from resonance sounds was at a level that could be disregarded.
  • the noise level caused by cavitation was at the same level as that of the working example of the orifice 60 described above under the same measurement conditions as the working example (refer to the value of the comparative example in FIG. 3 ).
  • noise caused by resonance sounds can be brought down to an insignificant level by forming the orifice exit 63 wherein the diameter widens or the diameter does not change so as to form the second taper angle ⁇ smaller than the first taper angle ⁇ along the direction of refrigerant outflow from the orifice middle section 61.
  • the orifice middle section 72 is formed but an orifice exit is not as in the comparative example ( FIG. 4 )
  • resonance occurs in the refrigerant outflow tube 50, and the noise caused by resonance sounds reaches an extremely high level.
  • the present invention has a wide range of application in expansion valves which are provided to refrigerant circuits of refrigeration apparatuses and which depressurize liquid refrigerant.
  • Patent Literature 1 Japanese Laid-open Patent Application No. 2009-228689

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

Claims (4)

  1. Soupape de détente (1) pour la dépressurisation d'un liquide frigorigène dans un circuit réfrigérant d'un appareil de réfrigération, ladite soupape de détente comprenant un corps principal de soupape (10) dans lequel est pratiqué un siège de soupape (12) débouchant dans une chambre de soupape (11), et un corps de soupape (20) effectuant un mouvement alternatif relativement à la chambre de soupape ;
    la soupape de détente comprenant en outre un orifice (60) pratiqué dans le siège de soupape, et possédant une entrée d'orifice (61), dont le diamètre est le plus petit, une section intermédiaire de l'orifice (62), dont le diamètre s'élargit dans la direction de l'écoulement de liquide frigorigène depuis l'entrée de l'orifice, de façon à former un premier angle de conicité (α), et une partie d'orifice de sortie (63) dont le diamètre s'élargit, ou reste le même, dans la direction de l'écoulement de liquide frigorigène depuis la section intermédiaire de l'orifice, de façon à former un deuxième angle de conicité (β), inférieur au premier angle de conicité ;
    la soupape de détente (1) étant caractérisée en ce que
    une deuxième longueur de la direction du débit (L2) de la sortie de l'orifice (63) dans la direction de l'écoulement de liquide frigorigène est égale ou inférieure à la première longueur de la direction de l'écoulement (L1) de la section intermédiaire de l'orifice (62) dans la direction de l'écoulement de liquide frigorigène.
  2. Soupape de détente (1) selon la revendication 1, caractérisée en ce que :
    une première longueur de la direction de l'écoulement de la section intermédiaire de l'orifice (62) le long de la direction du débit de liquide frigorigène est égale au diamètre minimum de l'entrée de l'orifice (61) ou à plusieurs fois ce diamètre minimum.
  3. Soupape de détente (1) selon la revendication 1 ou 2, caractérisée en ce que :
    le premier angle de conicité mesure 10 degrés ou davantage et 60 degrés ou moins.
  4. Soupape de détente (1) selon une quelconque des revendications 1 à 3, caractérisée en ce que :
    un deuxième angle d'inclinaison formé par la sortie de l'orifice (63) et un plan perpendiculaire à la direction de l'écoulement de liquide frigorigène est supérieur à un premier angle d'inclinaison formé par la section intermédiaire de l'orifice (62) avec un plan perpendiculaire à la direction de l'écoulement de liquide frigorigène, et égal à 90 degrés ou moins.
EP11826895.2A 2010-09-24 2011-09-22 Détendeur Active EP2620724B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010213239A JP5563940B2 (ja) 2010-09-24 2010-09-24 膨張弁
PCT/JP2011/071574 WO2012039450A1 (fr) 2010-09-24 2011-09-22 Détendeur

Publications (3)

Publication Number Publication Date
EP2620724A1 EP2620724A1 (fr) 2013-07-31
EP2620724A4 EP2620724A4 (fr) 2014-03-19
EP2620724B1 true EP2620724B1 (fr) 2019-07-24

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Application Number Title Priority Date Filing Date
EP11826895.2A Active EP2620724B1 (fr) 2010-09-24 2011-09-22 Détendeur

Country Status (6)

Country Link
US (1) US20130175351A1 (fr)
EP (1) EP2620724B1 (fr)
JP (1) JP5563940B2 (fr)
CN (1) CN103097836B (fr)
ES (1) ES2751362T3 (fr)
WO (1) WO2012039450A1 (fr)

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JP5395775B2 (ja) * 2010-10-12 2014-01-22 株式会社鷺宮製作所 電動弁
JP5327351B2 (ja) * 2012-04-09 2013-10-30 ダイキン工業株式会社 空気調和装置
JP6280704B2 (ja) * 2013-07-23 2018-02-14 Ｋｙｂ株式会社 制御バルブ
CN103697177A (zh) * 2013-12-30 2014-04-02 浙江高中压阀门有限公司 一种氧化铝调节阀
CN104930762B (zh) * 2014-03-19 2019-04-19 浙江三花智能控制股份有限公司 电子膨胀阀
CN106795981A (zh) * 2014-10-08 2017-05-31 三菱电机株式会社 膨胀阀及使用膨胀阀的制冷循环装置
CN106711533B (zh) * 2015-07-17 2019-08-27 浙江三花汽车零部件有限公司 热交换装置
JP6633121B2 (ja) * 2018-04-12 2020-01-22 三菱電機株式会社 膨張弁、および、膨張弁を用いる冷凍サイクル装置
CN108709004A (zh) * 2018-07-23 2018-10-26 温州大阳科技有限公司 一种防止节流孔堵塞废水的废水电磁阀
CN111503290A (zh) * 2019-01-31 2020-08-07 浙江三花智能控制股份有限公司 电子膨胀阀
JP2019070449A (ja) * 2019-02-05 2019-05-09 株式会社鷺宮製作所 電動弁及び冷凍サイクルシステム
JP7386971B2 (ja) * 2020-04-09 2023-11-27 三菱電機株式会社 冷凍サイクル装置及び空気調和装置
JP7050347B2 (ja) * 2020-07-02 2022-04-08 株式会社不二工機 流量調整弁
CN217736277U (zh) * 2022-01-26 2022-11-04 浙江盾安人工环境股份有限公司 电子膨胀阀

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Also Published As

Publication number Publication date
JP5563940B2 (ja) 2014-07-30
JP2012067964A (ja) 2012-04-05
CN103097836A (zh) 2013-05-08
WO2012039450A1 (fr) 2012-03-29
US20130175351A1 (en) 2013-07-11
EP2620724A4 (fr) 2014-03-19
CN103097836B (zh) 2015-06-17
EP2620724A1 (fr) 2013-07-31
ES2751362T3 (es) 2020-03-31

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