WO2021106934A1 - パワーエレメント及びこれを用いた膨張弁 - Google Patents

パワーエレメント及びこれを用いた膨張弁 Download PDF

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Publication number
WO2021106934A1
WO2021106934A1 PCT/JP2020/043824 JP2020043824W WO2021106934A1 WO 2021106934 A1 WO2021106934 A1 WO 2021106934A1 JP 2020043824 W JP2020043824 W JP 2020043824W WO 2021106934 A1 WO2021106934 A1 WO 2021106934A1
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WIPO (PCT)
Prior art keywords
diaphragm
power element
fulcrum
valve
valve body
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2020/043824
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English (en)
French (fr)
Japanese (ja)
Inventor
裕太郎 青木
潤哉 早川
祐亮 ▲高▼橋
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.)
Fujikoki Corp
Original Assignee
Fujikoki Corp
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 Fujikoki Corp filed Critical Fujikoki Corp
Priority to US17/778,967 priority Critical patent/US12092380B2/en
Priority to CN202080076730.3A priority patent/CN114667423B/zh
Priority to EP20893904.1A priority patent/EP4067714A4/en
Publication of WO2021106934A1 publication Critical patent/WO2021106934A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
    • 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
    • F16K31/002—Actuating devices; Operating means; Releasing devices actuated by temperature variation

Definitions

  • the present invention relates to a power element and an expansion valve using the power element.
  • a temperature-sensitive temperature expansion valve that adjusts the amount of refrigerant passing through according to the temperature has been used.
  • a power element that drives the valve body by the pressure of the enclosed working gas is adopted.
  • the power element provided in the expansion valve shown in Patent Document 1 is provided with an upper lid member forming a pressure working chamber in which a working gas is sealed between the diaphragm and the diaphragm, and a through hole in the center thereof and the diaphragm.
  • the diaphragm is made of a thin, flexible metal plate.
  • the valve body can be opened and closed via the stopper member and the working rod according to the amount of deformation, thereby adjusting the flow rate of the refrigerant passing through the expansion valve. It can be performed.
  • the shape of the power element is changed for each specification to obtain desired temperature / flow rate characteristics.
  • a slight change in characteristics requires a change in the type of parts of the power element, which leads to an increase in the cost of the expansion valve.
  • an object of the present invention is to provide a power element capable of obtaining a desired temperature / flow rate characteristic while being inexpensive, and an expansion valve using the power element.
  • the power element according to the present invention is Diaphragm and An upper lid member that is joined to one side of the outer peripheral portion of the diaphragm and forms a pressure working chamber between the diaphragm and the diaphragm.
  • An annular fulcrum adjusting member joined to the other side of the outer peripheral portion of the diaphragm, It has a receiving member that is joined to the fulcrum adjusting member and forms a refrigerant inflow chamber with the diaphragm. The diaphragm can be brought into contact with the fulcrum of the fulcrum adjusting member.
  • FIG. 1 is a schematic cross-sectional view schematically showing an example in which the expansion valve in the present embodiment is applied to a refrigerant circulation system.
  • FIG. 2 is an enlarged cross-sectional view of the power element of the first embodiment.
  • FIG. 3 is an exploded view of the power element of the first embodiment.
  • FIG. 4 is an enlarged cross-sectional view of the power element of the first modification.
  • FIG. 5 is an enlarged cross-sectional view of the power element of the second modification.
  • FIG. 6 is a diagram showing the temperature / flow rate characteristics of the expansion valve using the power element of the first embodiment.
  • FIG. 7 is an enlarged cross-sectional view of the power element of the second embodiment.
  • FIG. 8 is a schematic cross-sectional view showing an expansion valve according to the third embodiment.
  • FIG. 9 is a cross-sectional view of the power element according to the third embodiment.
  • FIG. 10 is an enlarged cross-sectional view showing a portion B of FIG. 8 in the third embodiment.
  • FIG. 1 is a schematic cross-sectional view schematically showing an example in which the expansion valve 1 in the present embodiment is applied to the refrigerant circulation system 100.
  • the expansion valve 1 is fluidly connected to the compressor 101, the condenser 102, and the evaporator 104.
  • L be the axis of the expansion valve 1.
  • the expansion valve 1 includes a valve body 2 having a valve chamber VS, a valve body 3, an urging device 4, an operating rod 5, and a power element 8.
  • the valve body 2 includes a first flow path 21, a second flow path 22, an intermediate chamber 221 and a return flow path (also referred to as a refrigerant passage) 23 in addition to the valve chamber VS.
  • the first flow path 21 is a supply-side flow path, and the refrigerant is supplied to the valve chamber VS via the supply-side flow path.
  • the second flow path 22 is a discharge side flow path, and the fluid in the valve chamber VS is discharged to the outside of the expansion valve through the valve through hole 27, the intermediate chamber 221 and the discharge side flow path.
  • the first flow path 21 and the valve chamber VS communicate with each other by a connecting path 21a having a smaller diameter than the first flow path 21.
  • the valve chamber VS and the intermediate chamber 221 communicate with each other via a valve seat 20 and a valve through hole 27.
  • the actuating rod insertion hole 28 formed above the intermediate chamber 221 has a function of guiding the actuating rod 5, and the annular recess 29 formed above the actuating rod insertion hole 28 has a function of accommodating the ring spring 6.
  • the ring spring 6 abuts a plurality of spring pieces on the outer circumference of the operating rod 5 to apply a predetermined urging force.
  • the valve body 3 is arranged in the valve chamber VS.
  • the valve body 3 When the valve body 3 is seated on the valve seat 20 of the valve body 2, the flow of the refrigerant in the valve through hole 27 is restricted. This state is called a non-communication state. However, even when the valve body 3 is seated on the valve seat 20, a limited amount of refrigerant may flow. On the other hand, when the valve body 3 is separated from the valve seat 20, the flow of the refrigerant passing through the valve through hole 27 increases. This state is called a communication state.
  • the operating rod 5 is inserted into the valve through hole 27 with a predetermined gap.
  • the lower end of the operating rod 5 is in contact with the upper surface of the valve body 3.
  • the upper end of the operating rod 5 is fitted in the fitting hole 84c of the stopper member 84, which will be described later.
  • the operating rod 5 can press the valve body 3 in the valve opening direction against the urging force of the urging device 4. When the operating rod 5 moves downward, the valve body 3 is separated from the valve seat 20 and the expansion valve 1 is opened.
  • the urging device 4 has a coil spring 41 in which a wire rod having a circular cross section is spirally wound, a valve body support 42, and a spring receiving member 43.
  • valve body support 42 is attached to the upper end of the coil spring 41, and a spherical valve body 3 is welded to the upper surface thereof, and both are integrated.
  • the spring receiving member 43 that supports the lower end of the coil spring 41 is screwable with respect to the valve body 2, and has a function of sealing the valve chamber VS and a function of adjusting the urging force of the coil spring 41. ..
  • FIG. 2 is an enlarged cross-sectional view of the power element 8.
  • FIG. 3 is an exploded view of the power element 8.
  • the power element 8 includes a stopper 81, an upper lid member 82, a diaphragm 83, a fulcrum adjusting member 85, a receiving member 86, and a stopper member 84.
  • the upper lid member 82 side is the upper side and the receiving member 86 side is the lower side.
  • the upper lid member 82 is formed, for example, by molding a metal plate material by pressing.
  • the upper lid member 82 has an annular outer plate portion 82b, an outer tapered portion 82c connected to the inner circumference of the outer plate portion 82b and facing upward, and an annular intermediate plate portion connected to the inner circumference of the outer tapered portion 82c. It has an 82d, an inner tapered portion 82e connected to the inner circumference of the intermediate plate portion 82d and directed upward, and a top portion 82f connected to the inner circumference of the inner tapered portion 82e.
  • An opening 82a is formed in the center of the top portion 82f, and can be sealed by a stopper 81.
  • the receiving member 86 facing the upper lid member 82 is formed, for example, by molding a metal plate material by pressing.
  • the receiving member 86 includes a flange portion 86a having an outer diameter substantially the same as the outer diameter of the outer plate portion 82b of the upper lid member 82, a conical portion 86b connected to the inner circumference of the flange portion 86a and facing downward, and a conical portion 86b. It has an annular inner plate portion 86c connected to the inner circumference of the inner circumference and a hollow cylindrical portion 86d connected to the inner circumference of the inner plate portion 86c.
  • a male screw 86e is formed on the outer circumference of the hollow cylindrical portion 86d.
  • a female screw 2c screwed into the male screw 86e is formed on the inner circumference of the recess 2a of the valve body 2 to which the hollow cylindrical portion 86d is attached.
  • the diaphragm 83 arranged between the upper lid member 82 and the fulcrum adjusting member 85 is made of a thin and flexible metal (for example, SUS) plate material, and has an outer diameter of the upper lid member 82 and the receiving member 86. Has almost the same outer diameter as.
  • the diaphragm 83 has an outer peripheral portion 83a sandwiched between the upper lid member 82 and the fulcrum adjusting member 85, and a central portion 83b that abuts on the stopper member 84. Further, the diaphragm 83 is coaxial with the axis O between the outer peripheral portion 83a and the central portion 83b, and has a plurality of upper ring-shaped portions 83c protruding upward and a plurality of lower ring-shaped portions protruding downward. Parts 83d are provided alternately along the radial direction. In the present embodiment, in the cross section shown in FIG.
  • the upper ring-shaped portion 83c and the lower ring-shaped portion 83d have a periodic shape such that a substantially sine curve is drawn, but the peripheral groove-shaped upper ring-shaped portion having a semicircular cross section.
  • the lower ring-shaped portion may be formed independently on the flat plate.
  • the fulcrum adjusting member 85 is formed in a substantially annular shape having an outer diameter substantially equal to that of the diaphragm 83 by molding a metal plate material such as SUS by pressing. More specifically, the fulcrum adjusting member 85 includes an annular flat plate portion 85a having a wider radial width than the flange portion 86a of the receiving member 86 and a supporting curved surface portion that is connected to the inner circumference of the annular flat plate portion 85a and faces downward. It has 85b and. It is preferable that the annular flat plate portion 85a and the support curved surface portion 85b are connected via a smooth curved surface.
  • the annular flat plate portion 85a is sandwiched and held between the outer peripheral portion 83a of the diaphragm 83 and the flange portion 86a of the receiving member 86. It is desirable that the hardness of the fulcrum adjusting member 85 is lower than the hardness of the receiving member 86, and it is desirable that the hardness be lower than the hardness of the diaphragm 83. As a result, when a foreign matter enters the vicinity of the fulcrum of the fulcrum adjusting member 85, the foreign matter is buried in the surface of the fulcrum adjusting member 85, so that damage to the diaphragm 83 can be suppressed.
  • the stopper member 84 includes a cylindrical main body 84a, a disk portion 84b connected to the upper end of the main body 84a and extending in the radial direction, and a bag hole-shaped fitting hole 84c formed in the center of the lower surface of the main body 84a.
  • the central top surface of the disk portion 84b is in contact with the lower surface of the central portion 83b of the diaphragm 83.
  • the outer peripheral portion of the disk portion 84b other than the central top surface is lower than the central top surface to form the outer peripheral step portion 84d.
  • the working gas is sealed in the space (pressure operating chamber PO, see FIG. 1) surrounded by the upper lid member 82 and the diaphragm 83, and then the opening 82a is closed by the plug 81.
  • the stopper 81 is fixed to the upper lid member 82 by projection welding or the like.
  • the diaphragm 83 receives pressure in a form of projecting toward the receiving member 86 due to the working gas sealed in the pressure operating chamber PO, the lower space (refrigerant inflow chamber) surrounded by the diaphragm 83 and the receiving member 86.
  • the central portion 83b of the diaphragm 83 comes into contact with the central top surface of the stopper member 84 arranged in the LS (see FIG. 1).
  • the disk portion 84b of the stopper member 84 is held between the diaphragm 83 and the inner plate portion 86c of the receiving member 86.
  • the axis O is aligned with the axis L, and the male screw 86e on the outer periphery of the lower end of the hollow cylindrical portion 86d of the receiving member 86 is attached to the valve body. It is screwed into the female screw 2c formed on the inner circumference of the recess 2a of 2.
  • the male screw 86e of the hollow cylindrical portion 86d is screwed with respect to the female screw 2c, the inner plate portion 86c of the receiving member 86 comes into contact with the upper end surface of the valve body 2. As a result, the power element 8 can be fixed to the valve body 2.
  • a packing PK is interposed between the power element 8 and the valve body 2 to seal the space in the recess 2a connected to the lower space LS to prevent the refrigerant from leaking from the recess 2a.
  • the lower space LS of the power element 8 communicates with the return flow path 23 via the communication hole 2b.
  • the refrigerant pressurized by the compressor 101 is liquefied by the condenser 102 and sent to the expansion valve 1. Further, the refrigerant adiabatically expanded by the expansion valve 1 is sent to the evaporator 104, and the evaporator 104 exchanges heat with the air flowing around the evaporator. The refrigerant returning from the evaporator 104 is returned to the compressor 101 side through the expansion valve 1 (more specifically, the return flow path 23). At this time, by passing through the evaporator 104, the fluid pressure in the second flow path 22 becomes larger than the fluid pressure in the return flow path 23.
  • High-pressure refrigerant is supplied to the expansion valve 1 from the condenser 102. More specifically, the high-pressure refrigerant from the condenser 102 is supplied to the valve chamber VS via the first flow path 21.
  • valve body 3 When the valve body 3 is seated on the valve seat 20 (in a non-communication state), it is sent from the valve chamber VS to the evaporator 104 through the valve passage hole 27, the intermediate chamber 221 and the second flow path 22. The flow rate of the refrigerant is limited. On the other hand, when the valve body 3 is separated from the valve seat 20 (in the state of communication), the valve chamber VS passes through the valve passage hole 27, the intermediate chamber 221 and the second flow path 22 to the evaporator 104. The flow rate of the delivered refrigerant increases. Switching between the closed state and the open state of the expansion valve 1 is performed by the operating rod 5 connected to the power element 8 via the stopper member 84.
  • a pressure operating chamber PO and a lower space LS partitioned by a diaphragm 83 are provided inside the power element 8. Therefore, when the working gas in the pressure working chamber PO is liquefied, the diaphragm 83 rises, so that the stopper member 84 and the working rod 5 move upward according to the urging force of the coil spring 41. On the other hand, when the liquefied working gas is vaporized, the diaphragm 83 and the stopper member 84 are pressed downward, so that the working rod 5 moves downward. In this way, the expansion valve 1 is switched between the open state and the closed state.
  • the lower space LS of the power element 8 communicates with the return flow path 23. Therefore, the volume of the working gas in the pressure working chamber PO changes according to the temperature and pressure of the refrigerant flowing through the return flow path 23, and the working rod 5 is driven.
  • the amount of the refrigerant supplied from the expansion valve 1 toward the evaporator 104 is automatically adjusted according to the temperature and pressure of the refrigerant returning from the evaporator 104 to the expansion valve 1. It will be adjusted.
  • the operation of the fulcrum adjusting member 85 will be described.
  • the diaphragm 83 is displaced toward the upper lid member 82 side or the receiving member 86 side across the neutral position according to the volume change of the working gas in the pressure working chamber PO.
  • the "neutral position” means a position where the diaphragm does not receive a reaction force from the fulcrum on the upper lid member side or the fulcrum on the fulcrum adjusting member side.
  • the "fulcrum on the upper lid member side” means a portion where the diaphragm is stopped (not displaced toward the upper lid member side) by abutting against the upper lid member and displaced toward the upper lid member side when the diaphragm is bent and displaced.
  • the fulcrum on the upper lid member 82 side is P1.
  • the "fulcrum on the fulcrum adjusting member side” means a portion where the diaphragm is stopped (not displaced to the receiving member side) by contacting the fulcrum adjusting member when the diaphragm is bent and displaced, and the receiving member side.
  • the fulcrum on the fulcrum adjusting member 85 side is P2 on the support curved surface portion 85b. When the fulcrum P2 is connected along the entire circumference, it becomes a circle centered on the axis O, and its diameter (referred to as the fulcrum diameter) is ⁇ 1.
  • the support curved surface portion 85b of the fulcrum adjusting member 85 projects inward from the flange portion 86a of the receiving member 86. If the fulcrum adjusting member 85 is not provided, the diaphragm 83 comes into direct contact with the receiving member 86, so that a fulcrum (a fulcrum on the receiving member side) is generated on the receiving member 86 instead of the fulcrum on the fulcrum adjusting member side.
  • the diameter of the fulcrum on the receiving member side at this time is clearly larger than the fulcrum diameter ⁇ 1 on the fulcrum adjusting member side. That is, by providing the fulcrum adjusting member 85, there is an effect of reducing the fulcrum diameter.
  • FIG. 4 is an enlarged cross-sectional view of the power element 8A of the first modification.
  • the shape of the fulcrum adjusting member 85A is changed with respect to the power element 8 of the first embodiment. More specifically, with respect to the first embodiment, the radial width of the annular flat plate portion 85Aa is widened toward the inner peripheral side. As a result, the fulcrum on the fulcrum adjusting member 85A side becomes P3 on the support curved surface portion 85Ab, and the fulcrum diameter thereof becomes ⁇ 2. At this time, ⁇ 1> ⁇ 2. Since the other configurations are the same as those in the above-described embodiment, the same reference numerals are given and duplicate description will be omitted.
  • FIG. 5 is an enlarged cross-sectional view of the power element 8B of the second modification.
  • the shape of the fulcrum adjusting member 85B is further changed with respect to the power element 8A of the first modification. More specifically, with respect to the first modification, the annular flat plate portion 85Ba is the same, but the support curved surface portion 85Bb is extended toward the axis O side while following the shape of the diaphragm 83.
  • the fulcrum P4 on the fulcrum adjusting member 85B side becomes the end portion of the support curved surface portion 85Ab, and the fulcrum diameter thereof becomes ⁇ 3.
  • FIG. 6 is a graph showing the temperature / flow rate characteristics of the expansion valve 1, in which the vertical axis represents the refrigerant flow rate and the horizontal axis represents the temperature of the power element.
  • the expansion valve 1 can control the temperature of the refrigerant circulation system 100 by increasing the flow rate of the refrigerant as the temperature of the power element increases.
  • what kind of refrigerant flow rate should be used at what temperature depends on the specifications of the refrigerant circulation system 100.
  • the fulcrum diameter of the fulcrum adjusting member 85A is reduced to ⁇ 2 ( ⁇ 1). Therefore, the temperature / flow rate characteristics along the graph B shown by the alternate long and short dash line in FIG. 6 can be obtained, and the flow rate of the refrigerant decreases even at the same temperature of the power element as compared with the graph A. The reason will be explained below.
  • the diaphragm 83 displaced toward the receiving member 86 is supported by the fulcrum P3 of the fulcrum adjusting member 85A and deformed.
  • the diaphragm 83 is supported by the fulcrum P4 of the fulcrum adjusting member 85B and deformed, so that the fulcrum diameter of the fulcrum adjusting member 85B is ⁇ 3 ( ⁇ 2). And even smaller. Therefore, for the same reason, the temperature / flow rate characteristics along the graph C shown by the alternate long and short dash line in FIG. 6 can be obtained, and the flow rate of the refrigerant is further reduced even at the same power element temperature as compared with the graph B.
  • the support curved surface portion 85Bb can be further extended to the axis O side while following the shape of the diaphragm 83. This has the effect of further reducing the fulcrum diameter of the fulcrum adjusting member.
  • the inner peripheral end (fulcrum) P5 of the fulcrum adjusting member 85B is located between the diaphragm 83 and the outer peripheral step portion 84d of the stopper member 84, so that the fulcrum adjusting member
  • the 85B and the stopper member 84 can be installed so as to overlap each other in the axis O direction without interfering with each other. That is, by using the configuration shown by the dotted line in FIG. 5, the degree of freedom for reducing the fulcrum diameter is increased without causing interference with other parts.
  • the fulcrum adjusting members 85, 85A, 85B having different shapes are used.
  • different temperature / flow rate characteristics of the expansion valve can be obtained.
  • FIG. 7 is an enlarged cross-sectional view of the power element 8C of the second embodiment.
  • the shape of the fulcrum adjusting member 85C is changed with respect to the power element 8B of the second modification. More specifically, in the cross section of FIG. 7, an outer convex portion 85Cc and an inner convex portion 85Cd forming an annular convex curved surface are provided on the support curved surface portion 85Cb of the fulcrum adjusting member 85C, respectively. Since the other configurations are the same as those of the above-described embodiment, the same reference numerals are given and duplicate description will be omitted.
  • the diaphragm 83 When the diaphragm 83 is displaced from the upper lid member 82 side to the receiving member 86 side, it first comes into contact with the outer convex portion 85Cc (shown by the dotted line in FIG. 7). In such a case, the fulcrum on the fulcrum adjusting member 85C side becomes P6 on the outer convex portion 85Cc, and the fulcrum diameter thereof becomes ⁇ 4. Further, when the diaphragm 83 is displaced toward the receiving member 86 side, it then abuts on the inner convex portion 85Cd (shown by a solid line in FIG. 7). In such a case, the fulcrum on the fulcrum adjusting member 85C side becomes P7 on the inner convex portion 85Cd, and the fulcrum diameter thereof becomes ⁇ 5 ( ⁇ 4).
  • the fulcrum P6 on the fulcrum adjusting member 85C side can be used to obtain characteristics similar to those of the graph B. Further, at a predetermined temperature or higher, by using the fulcrum P7 shifted inward in the radial direction from the fulcrum P6, characteristics similar to those of the graph C can be obtained.
  • the number of fulcrums is two, but three or more fulcrums different in the radial direction may be used.
  • FIG. 8 is a schematic cross-sectional view showing the expansion valve 1D in the third embodiment.
  • FIG. 9 is a cross-sectional view of the power element 8D according to the third embodiment.
  • FIG. 10 is an enlarged cross-sectional view showing a portion B of FIG. 8 in the third embodiment.
  • the expansion valve 1D shown in FIG. 8 differs from the expansion valve 1 according to the first embodiment in the upper configuration of the power element 8D and the valve body 2D. That is, in the present embodiment, the power element 8D and the valve body 2D are not connected by screwing the screws, and the two are connected by caulking. Since the other configurations are the same as those in the first embodiment, the same reference numerals are given and duplicate description will be omitted.
  • the power element 8D includes a stopper 81, an upper lid member 82, a diaphragm 83, a receiving member 86D, a fulcrum adjusting member 85, and a stopper member 84.
  • the upper lid member 82 side is the upper side and the receiving member 86D side is the lower side.
  • the stopper member may not be provided.
  • the configuration of the receiving member 86D is mainly different from that of the power element 8 in the first embodiment.
  • the other plugs 81, the upper lid member 82, the diaphragm 83, the fulcrum adjusting member 85, and the stopper member 84 have basically the same configuration except that the shapes of the details are different. Is omitted.
  • the receiving member 86D formed by molding a metal plate material by pressing is connected to a flange portion 86Da having an outer diameter substantially the same as the outer diameter of the outer plate portion 82b of the upper lid member 82 and the inner circumference of the flange portion 86Da. It has a hollow cylindrical portion 86Db that is provided and faces downward, and an annular inner plate portion 86Dc that is continuously provided on the inner circumference of the lower end of the hollow cylindrical portion 86Db.
  • the inner plate portion 86Dc includes a central opening 86Dd into which the main body 84a of the stopper member 84 is fitted.
  • the outer plate portion 82b of the upper lid member 82, the outer peripheral portion 83a of the diaphragm 83, and the annular portion of the fulcrum adjusting member 85 are formed.
  • the flat plate portion 85a and the flange portion 86Da of the receiving member 86D are overlapped in this order and pressed in the axial direction, and the outer periphery thereof is welded by, for example, TIG welding, laser welding, plasma welding, etc. to form the welded portion W over the entire circumference. And integrate these.
  • the working gas is sealed in the space surrounded by the upper lid member 82 and the diaphragm 83, the opening 82a is sealed with the stopper 81, and further projection welding or the like is used.
  • the stopper 81 is fixed to the upper lid member 82. With the above, the power element 8D is assembled.
  • the valve body 2D formed of a metal such as aluminum includes a circular tube portion 2d extending from the upper end thereof.
  • the inner diameter of the circular tube portion 2d is equal to or slightly larger than the outer diameter of the power element 8D.
  • the circular tube portion 2d Before assembling the power element 8D to the valve body 2D, the circular tube portion 2d has a cylindrical shape centered on the axis L (FIG. 8) as shown by the dotted line.
  • an annular packing PK is arranged on the step portion 2e of the valve body 2D, brought close to the valve body 2D from the receiving member 86D side, and the power element 8D is inside the circular tube portion 2d. To fit. At this time, the packing PK is sandwiched between the inner plate portion 86Dc and the step portion 2e.
  • the expansion valve 1D shown in FIG. 8 can also be incorporated into the refrigerant circulation system 100 shown in FIG. 1, and exhibits the same function as the expansion valve 1 according to the first embodiment.
  • the present invention is not limited to the above-described embodiment.
  • any component of the above-described embodiment can be modified.
  • any component can be added or omitted in the above-described embodiment.
  • Valve body 3 Valve body 4: Basis device 5: Actuating rod 6: Ring spring 8, 8A, 8B, 8C, 8D: Power element 20: Valve seat 21: First flow Road 22: Second flow path 221: Intermediate chamber 23: Return flow path 27: Valve through hole 28: Actuating rod insertion hole 29: An annular recess 41: Coil spring 42: Valve body support 43: Spring receiving member 81: Plug 82: Upper lid member 83: Diaphragm 84: Stopper member 85, 85A, 85B, 85C: Supporting point adjusting member 86, 86D: Receiving member 100: Refrigerant circulation system 101: Compressor 102: Condenser 104: Evaporator VS: Valve chamber P1: On the upper lid member side Support points P2 to P7: Support points on the fulcrum adjustment member side

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
  • Temperature-Responsive Valves (AREA)
PCT/JP2020/043824 2019-11-25 2020-11-25 パワーエレメント及びこれを用いた膨張弁 Ceased WO2021106934A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US17/778,967 US12092380B2 (en) 2019-11-25 2020-11-25 Power element and expansion valve using same
CN202080076730.3A CN114667423B (zh) 2019-11-25 2020-11-25 动力元件以及使用了该动力元件的膨胀阀
EP20893904.1A EP4067714A4 (en) 2019-11-25 2020-11-25 Power element and expansion valve using same

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Application Number Priority Date Filing Date Title
JP2019-212470 2019-11-25
JP2019212470A JP2021085548A (ja) 2019-11-25 2019-11-25 パワーエレメント及びこれを用いた膨張弁

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WO2021106934A1 true WO2021106934A1 (ja) 2021-06-03

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US (1) US12092380B2 (enExample)
EP (1) EP4067714A4 (enExample)
JP (2) JP2021085548A (enExample)
CN (1) CN114667423B (enExample)
WO (1) WO2021106934A1 (enExample)

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US20220412617A1 (en) 2022-12-29
CN114667423B (zh) 2024-07-26
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JP2021085548A (ja) 2021-06-03
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