WO2021218845A1 - Vanne de détente électronique - Google Patents

Vanne de détente électronique Download PDF

Info

Publication number
WO2021218845A1
WO2021218845A1 PCT/CN2021/089572 CN2021089572W WO2021218845A1 WO 2021218845 A1 WO2021218845 A1 WO 2021218845A1 CN 2021089572 W CN2021089572 W CN 2021089572W WO 2021218845 A1 WO2021218845 A1 WO 2021218845A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
port
electronic expansion
cavity
diameter
Prior art date
Application number
PCT/CN2021/089572
Other languages
English (en)
Chinese (zh)
Inventor
魏先让
沈自成
Original Assignee
浙江三花智能控制股份有限公司
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 浙江三花智能控制股份有限公司 filed Critical 浙江三花智能控制股份有限公司
Publication of WO2021218845A1 publication Critical patent/WO2021218845A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/36—Valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/42—Valve seats
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • This application relates to the technical field of refrigeration control, and in particular to electronic expansion valves.
  • the refrigeration system includes a compressor, a throttling element, two heat exchangers, and other parts.
  • the throttling element can use an electronic expansion valve to adjust the throttling of the refrigerant.
  • the use of an electronic expansion valve can achieve relatively precise control and improve system energy efficiency.
  • the electronic expansion valve generally includes a first port and a second port.
  • the refrigerant can flow in from the first port and flow out from the second port, or flow in from the second port and flow out from the first port.
  • a certain amount of noise may be generated. Improving the noise of the refrigerant passing through the electronic expansion valve is a technical topic that has been studied by related technicians of electronic expansion valves and refrigeration systems for a long time.
  • the object of the present invention is to provide an electronic expansion valve for improving the noise problem of refrigerant flowing through the electronic expansion valve.
  • an embodiment of the present invention adopts the following technical solutions:
  • An electronic expansion valve includes a valve seat, a valve body part, a valve core, a porous part, and a guide part.
  • the valve body part includes a valve body, and the valve body is fixedly connected to the valve seat; the valve seat includes a valve.
  • the electronic expansion valve includes a first valve cavity and a second valve cavity, the first valve cavity is located on the relatively upper side of the valve mouth, and the second valve cavity is located on the relatively lower side of the valve mouth;
  • the electronic expansion valve is provided with a valve port at the valve port, and the valve port can communicate with the first valve cavity and the second valve cavity;
  • the electronic expansion valve has a first interface and a second interface, the first An interface is in communication with the first valve cavity, and the second interface is in communication with the second valve cavity;
  • the valve core is at least partially located in the first valve cavity, and the valve core is used in conjunction with the valve port
  • the diameter of the valve port is smaller than the diameter of the second interface, and the diameter of the second interface is smaller than the diameter of the second valve cavity;
  • the guide member is fixedly connected to the valve seat, the porous member is at least mostly located in the first valve cavity, and one end of the cylindrical portion directly or indirectly abuts the guide member, and the other end of the porous member is in
  • valve chambers are provided in the electronic expansion valve, which are respectively located on both sides of the valve port.
  • the first valve chamber and the second valve chamber can communicate through the valve port, so that when the refrigerant is throttled in the first flow direction, the refrigerant section After the flow, it flows out to the second valve cavity, which has a relatively large space, and a porous part is arranged above the valve port, which can relatively improve the flow noise of the refrigerant.
  • FIG. 1 is a schematic structural diagram of an electronic expansion valve according to a first embodiment provided by this application;
  • Fig. 2 is an enlarged schematic diagram of part I of the electronic expansion valve shown in Fig. 1;
  • FIG. 3 is a schematic partial cross-sectional view of the electronic expansion valve shown in FIG. 1 including a valve seat and valve body parts;
  • Figure 4 is a schematic cross-sectional view of the valve seat
  • Fig. 5 is an enlarged schematic diagram of part II of Fig. 4;
  • FIG. 6 is a schematic diagram of an embodiment of another valve seat structure of this application.
  • FIG. 7 is a schematic structural diagram of an electronic expansion valve according to a second embodiment of this application.
  • valve seat component of the second embodiment is a schematic cross-sectional view of the valve seat component of the second embodiment
  • Fig. 9 is an enlarged schematic diagram of part III of Fig. 7;
  • FIG. 10 is a schematic diagram of another embodiment of the valve seat structure of this application.
  • FIG. 11 is a schematic structural diagram of an electronic expansion valve according to a third embodiment of this application.
  • Fig. 12 is an enlarged schematic diagram of part IV of Fig. 11;
  • FIG. 13 is a schematic diagram of the valve seat structure of the electronic expansion valve of the fourth embodiment.
  • Figure 14 is a partial cross-sectional view of another embodiment of the valve seat structure of this application.
  • FIG. 15 is a partial cross-sectional view of another embodiment of the valve seat structure of this application.
  • Figure 1 is a schematic structural view of the first embodiment of the electronic expansion valve
  • Figure 2 is a partial enlarged schematic view
  • Figure 3 is a partial cross-sectional schematic view of the electronic expansion valve of Figure 1, mainly including a valve seat and Part of the valve body part, so that the structure of the valve port can be clear
  • Figure 4 is a schematic cross-sectional view of the valve seat part.
  • the electronic expansion valve includes a valve seat 11, a valve body part 14, a connecting piece 15, a sleeve 16, a magnetic rotor assembly 17, a screw stem assembly 18, and a nut assembly 19.
  • the valve body part 14 includes a valve body 141, The seat 11 and the valve body 141 are fixedly connected by welding. At the same time, the valve seat 11 is fixedly connected with a first connecting pipe 121, and the valve body component 14 is fixedly connected with a second connecting pipe 122. In the direction shown in Figure 1, on the upper side of the valve seat 11, a connecting piece 15 is provided.
  • the connecting piece 15 is roughly in the shape of a cup with an open bottom and has an opening at the bottom. The connecting piece 15 is fixedly connected to the valve seat 11.
  • valve seat is connected with the sleeve through a connecting piece.
  • a step can be provided on the upper side of the valve seat 11, and the bottom opening of the connecting piece 15 can be matched with the step, and the two can be welded to fix them, or the two can be fixed relative to each other first, such as clamping and then welding. Fixed and so on.
  • a sleeve 16 is also provided on the upper side of the connecting piece 15.
  • the sleeve 16 and the connecting piece 15 can be fixed by welding. In this way, the sleeve 16, the connecting piece 15, and the valve seat 11 are fixedly connected.
  • the inner space is provided with a magnetic rotor assembly 17, a screw valve core assembly 18, and a nut assembly 19.
  • the connecting piece 15 is not necessary.
  • the sleeve 16 can also be directly fixedly connected to the valve seat 11, or other parts can be fixed. For example, the outer edge of the valve seat 11 is directly extended upwards and then welded to the sleeve 16 to be fixed.
  • the magnetic rotor assembly 17 can be rotated by inducing the electromagnetic force of the electromagnetic coil.
  • the magnetic rotor assembly 17 includes a magnetic rotor 171 and a connecting plate 172 fixedly connected or integrally provided with the magnetic rotor 171.
  • the connecting plate 172 can be used as an insert to form a magnetic ⁇ 171 ⁇ Rotor 171.
  • the screw valve core assembly 18 includes a screw rod 181, which is fixedly connected to the connecting plate 172. In this way, the screw rod 181 is connected to the magnetic rotor assembly 17 through the connecting plate 172 as a whole.
  • the screw rod 181 and the connecting plate 172 It can be fixedly connected by welding or connected by other fixed connection or limit connection methods such as clip connection and crimp connection.
  • the stop rod 173 is fixedly connected to the magnetic rotor assembly 17 and is generally located in an area substantially enclosed by the magnetic rotor 171.
  • the screw valve core assembly 18 includes a screw rod 181, a valve core 182, a valve core sleeve 183, a spring 184, a washer part 185, a retaining ring part 186, and a sleeve part 187.
  • the screw rod 181 and the valve core 182 realize a floating connection through the valve core sleeve 183.
  • the valve core sleeve 183 and the valve core 182 can be fixedly connected by welding.
  • the bottom end of the screw rod 181 is fixedly connected with a shaft sleeve member 187. The connection can be fixed by welding.
  • At least part of the valve core 182 is located in the first valve cavity A (see below).
  • valve core 182 When the electronic expansion valve is working, the valve core 182 can move a certain stroke relative to the valve port under the drive to cooperate with the valve port 1121 to adjust the flow rate. That is, during the operation of the electronic expansion valve, the valve core 182 can move up and down within a certain stroke relative to the valve port 112 to adjust the opening degree of the valve port 1121.
  • a retaining ring portion 186 and a gasket portion 185 are provided on the upper end surface of the valve core sleeve 183.
  • the retaining ring portion 186 in this embodiment is not limited to the C-shaped opening retaining ring shown in the figure, and opening retaining rings of other shapes can also be used.
  • the washer portion 185 in this embodiment is not limited to the circular ring-shaped washer in the figure, and can also be replaced by other retaining rings that can play the same role, for example, an open retaining ring can also be used instead.
  • the spring 184 is sheathed on the screw rod 181. Specifically, one end of the spring 184 abuts against the upper flange part 1811 of the screw rod, and the other end of the spring 184 abuts against the washer part 185. Under the action of the spring 184, the washer part 13 and the lower flange Part 1812 offset.
  • one end of the spring 14 abuts the upper flange portion 1811, including one end of the spring 184 directly abuts the upper flange portion 1551, and also includes one end of the spring 184 indirectly abuts the upper flange portion 1551, for example, the spring 184 and A retaining ring or other components are separately provided between the upper flange portions 1551.
  • the maximum outer diameter of the sleeve part 187 is greater than the minimum inner diameter of the central through hole of the valve core sleeve 183, so that after the assembly is completed, the valve core 182 cannot be separated from the screw rod 181.
  • valve core 182 When abutting against the valve port, the valve core 182 and the screw rod 181 can make a certain stroke of relative movement.
  • the detachment mentioned herein means that the sleeve part 183 and the screw rod 181 are separated into two separate parts without any restriction to each other, and not only that the two have no physical contact.
  • the nut assembly 19 includes a nut 191 and a connecting piece 192.
  • the nut 191 is fixedly connected to the connecting piece 192.
  • the connecting piece 192 can be stamped and formed from a metal plate.
  • the nut 191 is fixed to the sleeve 16 and/or the connecting piece 15 through a metal connecting piece 192. If provided, the nut 191 may be formed by injection molding using a non-metallic material with the connecting piece 192 as an insert, and the connecting piece 192 and the connecting piece 15 may be fixedly connected by welding. When the connecting piece is not provided, the connecting piece 192 and the valve seat 11 or the sleeve can be fixedly connected by welding.
  • the nut 191 has a through hole penetrating along its axial direction.
  • the nut is provided with internal threads on the inner side wall where the through hole is provided.
  • the outer peripheral surface of the screw rod 181 is provided with corresponding external threads.
  • a spring guide rail 1911 is provided on a part of the outer edge of the nut 191, and the spring guide rail 1911 is fixedly connected or connected with the nut 191 in a fixed position, so that the spring guide rail 1911 and the nut 191 realize relative positioning in both the axial direction and the circumferential direction, and the stop rod 173 rotates with the magnetic rotor assembly, and drives the slip ring 1912 to spirally slide along the spring guide 1911.
  • the nut assembly is provided with an upper stop part and a lower stop part, and the slip ring 1912 can abut against the upper stop part to stop rotating At the same time, the slip ring 1912 can abut against the lower stop and stop rotating.
  • the electronic expansion valve includes a guide portion 20, which is generally cylindrical.
  • a first outer edge portion 201 and a second outer edge portion 202 are provided on its outer periphery.
  • the diameter is smaller than the outer diameter of the second outer edge portion 202, and the outer diameter of the first outer edge portion 201 is adapted to the inner hole of the lower end of the nut 191.
  • the nut 191 is sleeved on the upper end of the guide portion 20 during assembly.
  • the first outer edge 201 can guide the assembly of the nut.
  • the outer diameter of the second outer edge portion 202 is adapted to the inner diameter of a part of the inner wall of the valve seat 11, and can be guided during assembly.
  • interference press fitting or welding can be used to make the guide portion 20 and the valve seat 11 Fixed connection.
  • the outer diameter of the first outer edge portion 201 shown in this embodiment is smaller than the outer diameter of the second outer edge portion 202, based on the fact that the inner diameter of the inner hole of the valve seat is smaller than the inner hole of the lower end of the nut.
  • the inner diameter of the inner hole of the valve seat may be set larger than the inner diameter of the lower end of the nut, or the inner diameters of the two may be set to be the same or approximately the same.
  • the guide portion 20 is also provided with a valve core guide portion 203, which matches the outer diameter of the valve core 182, so that the outer edge surface of the valve core 182 can move along the valve core guide portion 203.
  • the valve core guide portion 203 can provide good guidance and radial support to the valve core, which can relatively reduce the abnormal wear of the valve port caused by the swing of the valve core.
  • the above-mentioned first outer edge portion 201, second outer edge portion 202, and valve core guide portion 203 are all provided in a certain area or a certain part of the surface of the guide part 20, and this area or part can achieve corresponding
  • the guiding function is not a restriction on the shape of the guiding portion 20.
  • the guide portion 20 can be adapted to the size of the nut, the size and shape of the valve seat, as long as it includes the first outer edge portion 201 that can guide the nut and the first outer edge portion 201 that can guide the valve seat.
  • the two outer edge portions 202 and the valve core guide portion 203 that guides the valve core belong to the guide portion described in the embodiment of the present invention.
  • At least part of the guide part 20 is located in the first valve chamber A.
  • the lower end of the guide part changes the shape of the first valve chamber A, and can produce a certain amount of fluid flowing into the first valve chamber A. Influence, help to further reduce the noise of fluid flow.
  • the electronic expansion valve includes a valve seat 11, a valve body part 14, a first connecting tube 121, and a second connecting tube 122.
  • the valve seat 11, the valve body part 14, the first connecting tube 121 and the second connecting tube 122 are fixedly connected by welding.
  • the valve The seat 11 and the valve body 141 are fixedly connected by welding
  • the valve seat 11 and the first connecting pipe 121 are fixedly connected by welding
  • the valve body 141 and the second connecting pipe 122 are fixedly connected by welding.
  • the valve seat 11 has a valve port 112, and the valve port 112 is provided with a valve port 1121.
  • the electronic expansion valve has a first valve chamber A and a second valve chamber B.
  • a valve chamber A and a second valve chamber B can communicate through the valve port 1121.
  • the first valve chamber A is located on the upper side of the valve port 112, and the second valve chamber B is located on the lower side of the valve port 112.
  • the valve port 1121 The diameter D is smaller than the diameter H2 of the second port 1221, the diameter H2 of the second port 1221 is smaller than the diameter H1 of the second valve chamber B, and the diameter H3 of the first port 1211 is smaller than the diameter of the second valve chamber B. H1.
  • the second valve chamber B is not limited to the same diameter. If the diameter is different, the diameter H1 of the second valve chamber B refers to the maximum diameter. In this embodiment, the diameter H1 of the second valve chamber B, the diameter H3 of the first port 1211, and the diameter H2 of the second port 1221 satisfy the conditions: H1 ⁇ 1.3H3, H1 ⁇ 1.3H2.
  • valve body 141 is also provided with an inwardly flanged portion 1412 on the side wall portion 1411 of the valve body 141 to facilitate the mating connection with the second connecting pipe 122.
  • the material of the valve body 141 can be stainless steel.
  • the valve body is formed by drawing, punching or extrusion processing of a stainless steel plate or pipe.
  • the flow of refrigerant from the first port to the second port is defined as the first flow direction
  • the direction of refrigerant flowing from the second port to the first port is defined as the second flow direction.
  • the flow of refrigerant from the first connecting pipe to the second connecting pipe through the first valve cavity, valve port, and second valve cavity is defined as the first flow direction.
  • the refrigerant flows from the second connecting pipe through the second valve cavity, valve port, and first valve.
  • the flow of the cavity toward the first nozzle is defined as the second flow direction.
  • the valve port 112 of this embodiment includes a mating part 1123 and a flaring part 1124.
  • the mating part 1123 can be used to cooperate with the valve core and change the flow area of the electronic expansion valve as the valve core rises and falls.
  • the mating portion 1123 may be a straight section, that is, along the central axis, the inner diameter of the mating portion 1123 remains unchanged, which is convenient for processing. Of course, it is also allowed to set the inner diameter of the mating portion 1123 to gradually increase or decrease from top to bottom. Small frustum shape, but generally the cone angle does not exceed 5°, that is, the mating portion 1123 is closer to a straight section.
  • the matching portion 1123 is closer to the first valve cavity A than the flaring portion 1124, the flaring portion 1124 is located below the matching portion 1123, and the matching portion 1123 and the flaring portion 1124 are continuously arranged, please refer to FIG. 5, which is A cross-sectional view of the valve port 112 of this embodiment.
  • the thickness of the valve port 112 gradually increases radially outward from the bottom of the mating portion 1123 when the top of the valve port remains flat, that is, the valve port
  • the wall thickness of the portion 112 at the part of the mating portion 1123 is relatively thinnest, and gradually increases along the downward extending direction of the flaring portion 1124. In this way, the inner diameter of the end of the flaring portion 1124 close to the first valve cavity A is smaller than the inner diameter of the end of the flaring portion 1124 close to the second valve cavity B.
  • the wall thickness of the valve port 112 at the mating portion described above can also be understood as the height of the mating portion 1123, and the valve port 112 is expanding.
  • the wall thickness of the mouth can also be understood as the height of the flared portion 1124, so that h1 ⁇ h2.
  • the “flaring” mentioned in this specification refers to the diameter of the valve port, and the diameter of the valve port gradually increases along the direction of the center axis of the valve port.
  • the gradual increase trend mentioned here means that in terms of the inner diameter of the valve port as a whole, the inner diameter near the second valve cavity B is generally larger than the inner diameter near the first valve cavity A. However, along the top-down direction, it is allowed to reduce the inner diameter of a certain section, such as a groove facing the inner wall of the valve port.
  • the value of h1 can be between 0.15mm and 0.45mm, or even between 0.25mm and 0.35mm; the value of h2 can be between 2.5mm and 4.5mm, or even between 3.0mm and 4mm.
  • the flared portion 1124 is roughly flared in the longitudinal section shown in FIG.
  • the inner wall of the flared portion 1124 has two contour lines, and the two contour lines are straight lines, which define The highest point of one of the inner wall contour lines is X2 and the lowest point is X3.
  • the highest point of the other inner wall contour line is defined as Y2 and the lowest point is Y3.
  • the angle ⁇ , the value of ⁇ is between 40°-80°.
  • the passage space of the valve port 112 of the electronic expansion valve includes the space formed by the mating portion 1123 and the valve core and the space formed by the flaring portion 1124 and the valve core.
  • the valve port 112 further includes a protruding portion 1128 located below the flared portion 1124 and a tail portion 1129 located at the bottom of the entire valve port 112, based on the frustum-shaped inner wall of the flared portion 1124,
  • the protruding portion 1128 is in a protruding state in the direction of the central axis.
  • the tail portion 1129 can be set to be substantially in the same extending direction as the flaring portion 1124. In other words, it can be understood that the tail portion 1129 is an extension of the flaring portion 1124, and the protruding portion 1128 is located on the inner wall of the extended flaring portion, and faces the central axis.
  • the direction is convex.
  • the tail 1129 is not necessarily set to have the same angle value as the flared portion 1124.
  • the angle of the tail 1129 on the extension line of the cross section is 40°- The range of 80° is sufficient, and it can still ensure a better noise control effect.
  • the diameter of the valve port 112 (or roughly understood as the first The diameter of the second valve chamber B) is required, and the general electronic expansion valve on the market does not have a second valve chamber, and only connects an ordinary pipe to the valve port (the inner diameter usually does not exceed 8mm), then Limited by the inner diameter of the tube, it is impossible to meet the above values of h2 and ⁇ at the same time.
  • the diameter of the second valve cavity H1 roughly defined by the valve body is between 9mm-30mm, and even between 11mm-14mm. On this basis, the above-mentioned h2 can be easily achieved.
  • the value and the value of ⁇ is
  • the valve port structure provided in this embodiment can reduce noise to a certain extent, and in particular, the noise test result in the first flow direction is relatively good, and is better than the noise test result in the second flow direction.
  • the contour shape of the flaring portion 1124 can be changed.
  • FIG. 6, is a schematic diagram of another valve seat structure of the present application.
  • the flaring The portion 1124 is no longer in a standard cone shape, and its shape in the longitudinal section is also not linear.
  • the height of the flaring portion 1124 as a limit, it is located in a longitudinal section passing through the central axis of the valve seat.
  • the flaring portion 1124 has two inner wall contour lines, and the two contour lines are curved.
  • An example of a curve can actually use a variety of different curve shapes, or a combination of multiple curve shapes, a combination of curves and straight lines, and so on.
  • Section Q1 and the contour lines of the two wheel inner walls of the flaring part 1124 intersect at two points X1 and Y1 respectively. Connect X1 and X2 to obtain a straight line, and connect Y1 and Y2 to obtain another straight line.
  • the two straight lines have an angle of ⁇ , ⁇ The angle meets the condition: 40° ⁇ 1 ⁇ 80°.
  • the value of the height h4 from X1 to X2 in the vertical direction satisfies: h4 ⁇ 2.5mm.
  • the valve seat with this structure can also meet the noise requirements of the electronic expansion valve when applied to the first embodiment.
  • FIG. 7 is a schematic structural diagram of an electronic expansion valve according to a second embodiment of this application
  • FIG. 8 is a schematic cross-sectional view of the valve seat component of the second embodiment
  • FIG. 9 is a diagram of FIG. 8 Part III is an enlarged schematic diagram
  • FIG. 10 is a partial cross-sectional schematic diagram of another valve seat component.
  • the technical solution of this embodiment is to improve the structure of the valve cavity and the valve port to achieve the purpose of improving noise.
  • Other components of the electronic expansion valve such as magnetic rotor assembly, nut assembly, stop device, etc., are not limited here.
  • the technical solution of the present application does not specifically limit the structure of the above-mentioned components. Those skilled in the art will use the technical solutions disclosed herein. , It can be applied to all similar electronic expansion valve structures.
  • the magnetic rotor assembly 17, the screw valve core assembly 18, the connecting piece 15, the sleeve 16, the valve body member 14, the nut assembly 19, and the guide part 20 in this embodiment can all adopt the same structure as the first embodiment. This will not be repeated here.
  • the electronic expansion valve includes a valve seat 11a, a valve body part 14, a first connecting tube 121, and a second connecting tube 122.
  • the valve seat 11a, the valve body part 14, the first connecting tube 121, and the second connecting tube 122 are fixedly connected by welding.
  • the valve The seat 11a and the valve body 141 are fixedly connected by welding
  • the valve seat 11a and the first connecting pipe 121 are fixedly connected by welding
  • the valve body 141 and the second connecting pipe 122 are fixedly connected by welding.
  • the valve seat 11a has a valve port 112a
  • the valve port 112a is provided with a valve port 1121a.
  • the electronic expansion valve has a first valve chamber A and a second valve chamber B.
  • a valve chamber above the valve port 112a and The part communicating with the first port 1211 of the first connecting pipe 121 is the first valve chamber A, and the valve chamber below the valve seat and communicating with the second port 1221 of the second connecting pipe 122 is the second valve chamber B.
  • a valve chamber A and a second valve chamber B can communicate through the valve port 1121a.
  • the first valve chamber A is located on the upper side of the valve port 112a, and the second valve chamber B is located on the lower side of the valve port 112a.
  • the valve port 1121a The diameter D is smaller than the diameter H2 of the second port 1221, the diameter H2 of the second port 1221 is smaller than the diameter H1 of the second valve chamber B, and the diameter H3 of the first port 1211 is smaller than the diameter of the second valve chamber B. H1.
  • the second valve cavity B is not limited to the same diameter. If the diameter is different, the diameter H1 of the second valve chamber B refers to the maximum diameter.
  • the valve port 112a of this embodiment includes a mating part 1123a and a flaring part 1124a.
  • the mating part 1123a can be used to cooperate with the valve core and change the flow area of the electronic expansion valve as the valve core rises and falls.
  • the mating portion 1123a can be a straight section, that is, along the central axis, the inner diameter of the mating portion 1123a remains unchanged, which is convenient for processing. Of course, it is also allowed to set the inner diameter of the mating portion 1123a to gradually increase or decrease from top to bottom.
  • a transition portion 1122a is further provided above the mating portion 1123a. That is, the transition portion 1122a is located at the opposite top of the valve port portion 112a, the mating portion 1123a and the flaring portion 1124a are sequentially located below the transition portion 1122a, and the valve seat 11a is made of one-piece material.
  • the thickness of the valve port portion 112a gradually decreases at the transition portion 1122a, remains basically unchanged at the mating portion 1123a, and gradually increases at the flaring portion 1124a .
  • the gradual increase in thickness mentioned here means that the thickness of the valve port portion 112a gradually increases radially outward from the bottom of the mating portion 1123a.
  • the thickness of the valve port 112a at the transition portion 1122a mentioned above can also be understood as the height of the transition portion 1122a
  • the thickness of the valve port 112a at the mating portion 1123a can also be understood as the height of the mating portion 1123a
  • the thickness of the valve port 112a at the flaring portion 1124a can also be understood as the height of the flaring portion 1124a.
  • the “flaring” mentioned in this specification refers to the diameter of the valve port, along the center axis direction of the valve port, starting from the bottom of the mating portion 1123a, the diameter of the valve port gradually increases.
  • the gradual increase trend mentioned here refers to the overall inner diameter of the valve port, the inner diameter near the second valve cavity B is generally larger than the inner diameter near the first valve cavity A, but along the The top-down direction allows the inner diameter of a certain section to be reduced, such as setting a groove facing the inner wall of the valve port.
  • the value of h1 can be between 0.15mm-0.45mm, or even between 0.25mm-0.35mm; the value of h2 can be between 2.5mm-4.5mm, or even between 3.0mm-4mm; the value of h3 The value can be between 0.05mm-0.2mm, or even between 0.05mm-0.15mm.
  • the flared portion 1124a is roughly flared in the longitudinal section shown in FIG. 9, and the inner wall of the flared portion 1124a is as large as an angle of ⁇ at the extension line of the cross section, and the value of ⁇ is an acute angle, And between 40°-80°.
  • the transition portion 1122a is formed by chamfering the valve port toward the first valve cavity A, and the transition portion 1122a is arranged adjacent to the first valve cavity A. Since the height of the transition portion 1122a is relatively small, from an enlarged view, the cross-sectional shape may be linear or curved. In the longitudinal section shown in Fig.
  • the transition portion is a straight horn shape, and the transition portion 1122a is located at the extension line of the section as large as an angle of ⁇ , the value of ⁇ is an acute angle, and is at 40°- Between 80°.
  • the refrigerant flows in the first flow direction, the refrigerant passes through the transition portion 1122a, the mating portion 1123a, and the flared portion 1124a, which facilitates the diffusion of the refrigerant to the peripheral area, thereby improving the noise of the refrigerant flowing in the first flow direction .
  • the passage space of the valve port 112 of the electronic expansion valve includes a transition portion 1122a, a space formed by a mating portion 1123a and the valve core, and a space formed by a flaring portion 1124 and the valve core.
  • the refrigerant flows in the first flow direction, it flows through in sequence.
  • the crossing portion 1122a, the matching portion 1123a, and the flaring portion 1124 enter the second valve cavity B again.
  • the transition portion described above is not limited to a truncated cone shape, that is, the longitudinal section of the transition portion is not limited to a straight line.
  • Figure 10 is a partial cross-sectional view of another valve seat structure of this embodiment.
  • the contour line of the transition portion 1122a1 in the longitudinal section is curved. Since the height h5 of the transition portion is only between 0.05mm-0.2mm, Changing the straight line of the longitudinal section to an arc-shaped or curved section will not affect the technical effect of this embodiment.
  • the diameter of the valve port 112a (or roughly understandable It is required for the diameter of the second valve chamber B), and the general electronic expansion valve on the market does not have a second valve chamber, and only connects an ordinary pipe to the valve port (the inner diameter usually does not exceed 8mm) , It is limited by the inner diameter of the tube and cannot meet the above values of h2 and ⁇ at the same time.
  • the diameter of the second valve cavity H1 roughly defined by the valve body is between 9mm-30mm, and even between 11mm-14mm. On this basis, the above-mentioned h2 can be easily achieved.
  • the value and the value of ⁇ is
  • valve port structure provided by this embodiment can reduce noise to a certain extent, especially the noise test result in the second flow direction is relatively good, and is better than the noise test result in the first flow direction.
  • FIG. 11 is a schematic structural diagram of an electronic expansion valve according to a third embodiment of this application
  • FIG. 12 is an enlarged schematic diagram of part IV in FIG. 11.
  • the technical solution of this embodiment is to improve the structure of the valve cavity and the valve port to achieve the purpose of improving noise.
  • Other components of the electronic expansion valve such as magnetic rotor assembly, nut assembly, stop device, etc., are not limited here.
  • the technical solution of the present application does not specifically limit the structure of the above-mentioned components. Those skilled in the art will use the technical solutions disclosed herein. , It can be applied to all similar electronic expansion valve structures.
  • the magnetic rotor assembly 17, the screw valve core assembly 18, the connecting piece 15, the sleeve 16, the valve body member 14, the nut assembly 19, and the guide part 20 in this embodiment can all adopt the same structure as the first embodiment. This will not be repeated here.
  • the valve seat 11 of this embodiment also adopts the same structure as the first embodiment, including a valve port 112, and the valve port includes a matching portion 1123 and a flaring portion 1124.
  • the present embodiment further includes a porous member 21, which is at least mostly located in the first valve cavity A and relatively abuts or is fixedly connected to the valve seat.
  • the abutment mentioned here includes both direct abutment and indirect abutment.
  • adding a gasket between the porous component and the valve seat can be regarded as indirect abutment between the porous component and the valve seat.
  • the porous component 21 is open at both ends, and can be formed by sintering metal balls, such as sintering small copper balls.
  • This structure can withstand a certain pressure without falling off, chipping, or scattering.
  • a ring-shaped mounting groove 1125 can be provided on the top of the valve port 112 of the valve seat 11 outside the valve port.
  • the guide member 20 is installed, the guide member 20 is abutted with the porous member 21 by setting a predetermined dimensional tolerance, and a certain pressure is applied to the porous member 21 to fix the porous member 21 on the valve seat 11.
  • the abutment mentioned here also includes direct abutment or indirect abutment.
  • adding a gasket between the porous member and the guiding member can be regarded as indirect abutment between the porous member and the guiding member. Due to the existence of the installation groove 1125, the porous member 21 is not easily deviated from the valve seat, thereby making the structure more stable. After the refrigerant flows into the first valve cavity A from the first connecting pipe, it first passes through the porous member 21, then enters the valve port, and flows into the second valve cavity B.
  • the annular mounting groove 1125 may not be provided on the outside of the valve port, but the porous member 21 is directly placed on the top of the valve port, so that the ring of the cylindrical member 21 The shaped bottom directly abuts against the top plane of the valve port.
  • the porous component 21 can be formed by sintering small copper balls, and there is a relatively strong bonding force between the small copper balls, and it can also be prevented from dispersing or falling off under the condition of certain deformation.
  • the porous member 21 may also be formed by sintering stainless steel wire, that is, as long as a porous gap can be formed to allow the refrigerant to pass through.
  • the axial direction is limited to the height of the porous member 21, the first valve cavity A is separated by the porous member 21, and the space inside the porous member of the first valve cavity A passes through the valve port 1121 Connected with the second valve cavity A, the first valve cavity A is in direct communication with the first port 1211 in the space outside the porous component, and the first port 1211 and the second port are connected through the porous component 21, the valve port 1121, and the second valve cavity B .
  • the porous member 21 is formed by winding copper balls.
  • the refrigerant can pass through the gap formed between the copper balls of the porous member.
  • the porous member 21 can be further provided
  • the penetrating portion 211 penetrating the cylindrical wall portion of the penetrating portion 211 connects the inner cavity space of the porous member with the outer cavity space, which can reduce the risk of the porous member being blocked by impurities.
  • Figure 10 shows a schematic diagram of the through part 211.
  • the through part 211 is a number of notches provided at the top of the porous component. The advantage of this structure is that it can be directly formed during sintering.
  • the penetration portion 211 can be provided at the bottom of the porous member, or a notch can be used, or even on the side wall of the porous member. The way of punching and so on.
  • valve port structure provided by this embodiment can reduce noise to a certain extent, and the noise control effect in the first flow direction and the second flow direction is relatively good.
  • the electronic expansion valve described in the above three embodiments is provided with two valve chambers, which are respectively located on both sides of the valve port.
  • the first valve chamber and the second valve chamber can communicate through the valve port, so that when the refrigerant is throttled in the first flow direction , The refrigerant flows out to the second valve cavity after throttling, the second valve cavity has a relatively large space, combined with the valve port or the valve port combined with the porous part, the flow mode and flow space of the refrigerant are changed, thereby improving the refrigerant The flow noise.
  • the valve body described in each of the above embodiments can be formed by processing stainless steel material by stretching or extrusion, such as processing by plate or pipe, which can make processing relatively convenient and make the wall thickness of the valve body less than 1 mm.
  • the diameter mentioned in this article means that its cross-section is not limited to a circular shape.
  • the cross-section of the valve port is not limited to a circular shape, but can also include other shapes, such as the diameter of the second valve cavity, and its cross-section is not limited to a circular shape. .
  • the diameter H2 of the second port is greater than the diameter D of the valve port 1121
  • the diameter H1 of the second valve chamber B is greater than the diameter H2 of the second port connected by the second connecting pipe
  • the diameter H1 of the second valve chamber B is greater than the diameter H1 of the second port.
  • the diameter H3 of the first interface connected by a connecting pipe, and the diameter H2 of the second interface connected by the second connecting pipe is larger than the diameter D of the valve port 1121.
  • the through diameter is equivalent to the equivalent internal diameter, that is, the internal diameter value when the cross-sectional area is transformed into a circle with the same cross-sectional area, or the two have the same cross-sectional area, so that they have the same flow area.
  • the valve body has a bottom wall portion 1413, and the distance L from the bottom wall portion 1413 to the valve port is more than twice the diameter H2 of the second connecting pipe 122, that is, the second valve cavity B has sufficient height to reduce fluid noise Has a certain effect.
  • the valve core 182 includes an adjusting portion 1821 and a pointed portion 1822.
  • the adjusting portion 1821 and the pointed portion 1822 are approximately located at the bottom end of the valve core 182, wherein the pointed portion 1822 is located at the adjusting portion.
  • the cross-sectional contour line of the adjusting portion 1821 is roughly in a smoothly transitioned curve shape.
  • An annular gap is formed between the outer edge of the adjusting portion 1821 and the valve port 112 for the passage of refrigerant, and as the valve core 182 gradually moves upward, the cross-sectional contour line of the adjusting portion 1821 is a smooth transition curve, The above-mentioned annular gap will also change in size accordingly, and the flow rate is roughly adjusted in a proportional state, which is different from the linear adjustment state of the frustum-shaped valve core commonly used in this field. It should be noted that the cross-sectional contour line of the adjusting portion may be a combination of multiple curves.
  • An integrally structured pointed portion 1822 is provided at the bottom of the adjusting portion 1821, and the entire pointed portion 1822 protrudes downward from the bottom of the adjusting portion 1821.
  • the pointed part 1822 changes the shape of the annular gap formed between the valve core 182 and the valve port 112. Compared with the valve core without the pointed part, it can fill a part of the refrigerant flow path and reduce the refrigerant at the bottom of the valve core. There is the possibility of vortex, which helps to reduce the noise of refrigerant flow. It should be noted that the structure of the valve core can be applied to any of the above embodiments, that is, the valve core structure including the adjusting portion and the pointed portion is applied to the valve port structure of any embodiment to obtain better noise control. Effect.
  • FIG. 13 is a schematic diagram of a valve seat structure of an electronic expansion valve according to a fourth embodiment of the present invention. It should be noted that this embodiment is improved on the basis of the first embodiment. As a complete embodiment, it is only necessary to replace the valve seat member shown in FIG. 11 with that shown in FIG. 1 of the first embodiment. The valve seat part can be formed. In order to make the description not excessively lengthy, in this embodiment, other electronic expansion valve components other than the valve seat component will not be described. At the same time, it should be noted that the valve seat component of this embodiment can be applied to the second embodiment or the third embodiment.
  • the valve seat 11b of this embodiment includes a valve port 112b, and the valve port 112b includes a mating portion 1121b and a flaring portion 1122b.
  • the difference from the first embodiment is that the flaring portion 1122b extends to the valve The bottom end of the mouth 112b.
  • the thickness of the valve port portion 112b gradually increases at the flared portion 1122b.
  • the gradual increase in thickness mentioned here means that the thickness of the valve port portion 112b gradually increases radially outward from the bottom of the mating portion 1121b.
  • the thickness of the valve port 112b at the mating portion 1121b can also be understood as the height of the mating portion 1121b
  • the thickness of the valve port 112b at the flaring portion 1122b can also be It is understood as the height of the flared portion 1122b.
  • the "flaring” mentioned in this specification refers to the diameter of the valve port, along the center axis direction of the valve port, starting from the bottom of the mating portion 1122b, the diameter of the valve port gradually increases.
  • the value of h1 can be between 0.15mm and 0.45mm, or even between 0.25mm and 0.35mm; the value of h2 can be between 4.5mm and 6.5mm, or even between 5.0mm and 6mm.
  • the flared portion 1122b is roughly flared in the longitudinal section shown in FIG. 13, and along the longitudinal section of the valve port 112b passing through the central axis, the inner wall of the flared portion 1122b has two contour lines, two contours The line is a straight line.
  • intersection point of one of the inner wall contour lines and the mating part as X2 and the lowest point as X3
  • the connecting line of X2 and X3 There is an angle ⁇ between the connecting lines of Y2 and Y3, and the value of the angle ⁇ satisfies: 40° ⁇ 80°.
  • the diameter of the valve port 112b (or roughly understood as the first The diameter of the second valve chamber B) is required, and the general electronic expansion valve on the market does not have a second valve chamber, and only connects an ordinary pipe to the valve port (the inner diameter usually does not exceed 8mm), then Limited by the inner diameter of the tube, it is impossible to meet the above values of h2 and ⁇ at the same time.
  • the diameter of the second valve cavity H1 roughly defined by the valve body is between 9mm-30mm, and even between 11mm-14mm. On this basis, h2 can be easily selected. Value and the value of ⁇ .
  • the passage space of the valve port 112 of the electronic expansion valve includes the space formed by the fitting portion 1121b and the valve core, and the space formed by the flaring portion 1122b and the valve core.
  • the mating parts described in the first, second, and third embodiments can be understood as the mating parts of this embodiment, and the first and second embodiments
  • the flared portion described in the mode and the third embodiment is understood to be a part of the flared portion 1122b of this embodiment.
  • the contour shape of the flaring portion 1122b can be changed.
  • FIG. 14 is a schematic diagram of another valve seat structure of the present application.
  • the flaring portion 1122b is no longer a standard cone shape, and its shape in longitudinal section is not a straight line either.
  • the contour line of the inner wall of the flared portion 1122b is an irregular curve in the vertical and horizontal planes of the valve seat shown in the figure passing through the central axis.
  • the flared portion 1122b has two inner wall contours.
  • the value of the height h4 from X1 to X2 in the vertical direction satisfies: h4 ⁇ 2.5mm.
  • the valve seat of this structure applied to the first embodiment or the second embodiment can also meet the noise requirements of the electronic expansion valve. Due to space limitations, the application of the valve seat of this embodiment to the second embodiment will not be described in detail, namely It is equivalent to adding a transition part to the valve seat of this embodiment. It should be noted that along the direction of the center axis of the valve port, the diameter of the valve port has a gradually increasing trend. The gradually increasing trend mentioned here refers to the overall inner diameter of the valve port.
  • the inner diameter near the second valve cavity B is generally larger than the inner diameter near the first valve cavity A, but along the top-down direction, a certain section of the inner diameter is allowed to become smaller, such as a line facing the inner wall of the valve port The grooves and other situations.
  • FIG. 15 is a partial cross-sectional view of another valve seat structure of this application.
  • the contour line of the inner wall of the flared portion 1122b is a continuous arc in the vertical and horizontal planes of the valve seat shown in the figure passing through the central axis.
  • the flared portion 1122b has two inner wall contours.
  • Line define the intersection of one of the contour lines and the mating part as X2 and the lowest point as X3, define the intersection of the other contour line and the mating part as Y2 and the lowest point as Y3, with the height of the flaring part 1122b as the limit, at least There is a cross section Q1, the cross section Q1 and the contour line of the inner wall of the flaring portion 1122b intersect at two intersection points X1 and Y2, connect X1 and X2 to obtain a straight line, and connect Y1 and Y2 to obtain another straight line.
  • the two straight lines have The angle of ⁇ , the angle of ⁇ satisfies the condition: 40° ⁇ 80°.
  • the value of the height h4 from X1 to X2 in the vertical direction satisfies: h4 ⁇ 2.5mm.
  • the line of the inner wall contour line X2 and X3 of the flaring part, and the line of Y2 and Y3 have an angle of ⁇ .
  • X3 and Y3 are relatively closer to the outer side wall of the valve seat, and the angle of ⁇ will be greater than 80 °, but due to the presence of X1 and Y1 on the contour of the inner wall of the flared part, the angle of ⁇ meets the condition: 40° ⁇ 80°, and satisfies h4 ⁇ 2.5mm, which still has the effect of reducing noise.
  • the valve seat of this structure applied to the first embodiment or the second embodiment can also meet the noise requirements of the electronic expansion valve. Due to space limitations, the application of the valve seat of this embodiment to the second embodiment will not be described in detail, namely It is equivalent to adding a transition part to the valve seat of this embodiment.
  • the gradually increasing trend mentioned here refers to the overall inner diameter of the valve port.
  • the inner diameter near the second valve cavity B is generally larger than the inner diameter near the first valve cavity A, but along the top-down direction, a certain section of the inner diameter is allowed to become smaller, such as a line facing the inner wall of the valve port The grooves and other situations.

Landscapes

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

Abstract

La présente invention concerne une vanne de détente électronique comprenant une base de vanne, un composant de corps de vanne, un élément vanne, un composant poreux et un composant de guidage, le composant de corps de vanne comprenant un corps de vanne, et le corps de vanne est raccordé à demeure à la base de vanne ; la base de vanne comprend une partie orifice de vanne ; une première cavité de vanne et une seconde cavité de vanne sont en outre comprises, la première cavité de vanne étant située sur le côté opposé à la partie supérieure de la partie orifice de vanne, et la seconde cavité de vanne étant située sur le côté opposé à la partie inférieure de la partie orifice de vanne ; la partie orifice de vanne est pourvue d'un orifice de vanne qui est en communication avec la première cavité de vanne et la seconde cavité de vanne ; la vanne de détente électronique est pourvue d'un premier raccord et d'un second raccord, le premier raccord étant en communication avec la première cavité de vanne, et le second raccord étant en communication avec la seconde cavité de vanne ; l'élément de vanne est au moins partiellement situé dans la première cavité de vanne, et l'élément vanne coopère avec l'orifice de vanne pour régler l'écoulement de la vanne de détente électronique ; le diamètre de l'orifice de vanne est inférieur à celui du second raccord, et le diamètre du second raccord est plus petit que celui de la seconde cavité de vanne ; et le composant de guidage est raccordé à demeure à la base de vanne, au moins la majeure partie du composant poreux est située dans la première cavité de vanne, une extrémité d'une partie cylindrique vient directement ou indirectement en butée contre le composant de guidage, et l'autre extrémité du composant poreux vient en butée contre ou est raccordée à demeure à la base de vanne.
PCT/CN2021/089572 2020-04-26 2021-04-25 Vanne de détente électronique WO2021218845A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202010340932.6A CN113566459A (zh) 2020-04-26 2020-04-26 电子膨胀阀
CN202010340932.6 2020-04-26

Publications (1)

Publication Number Publication Date
WO2021218845A1 true WO2021218845A1 (fr) 2021-11-04

Family

ID=78157659

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2021/089572 WO2021218845A1 (fr) 2020-04-26 2021-04-25 Vanne de détente électronique

Country Status (2)

Country Link
CN (1) CN113566459A (fr)
WO (1) WO2021218845A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114352798B (zh) * 2022-01-26 2023-01-03 广东威灵电机制造有限公司 电子膨胀阀和制冷设备

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000081163A (ja) * 1998-07-01 2000-03-21 Shinkawa Denki Kk 調節弁を含む流体機器
CN103994231A (zh) * 2014-04-30 2014-08-20 吴俊云 一种电子膨胀阀
CN203963029U (zh) * 2014-04-30 2014-11-26 吴俊云 一种电子膨胀阀
CN106352139A (zh) * 2015-07-17 2017-01-25 株式会社鹭宫制作所 电动阀以及冷冻循环
CN206338987U (zh) * 2016-11-22 2017-07-18 广东美的暖通设备有限公司 电子膨胀阀和空调系统
CN106989193A (zh) * 2016-01-20 2017-07-28 株式会社不二工机 流量调整阀
CN107435753A (zh) * 2016-05-25 2017-12-05 浙江三花智能控制股份有限公司 电子膨胀阀及具有其的制冷设备
CN208794791U (zh) * 2018-04-29 2019-04-26 浙江新劲空调设备有限公司 一种电子膨胀阀

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000081163A (ja) * 1998-07-01 2000-03-21 Shinkawa Denki Kk 調節弁を含む流体機器
CN103994231A (zh) * 2014-04-30 2014-08-20 吴俊云 一种电子膨胀阀
CN203963029U (zh) * 2014-04-30 2014-11-26 吴俊云 一种电子膨胀阀
CN106352139A (zh) * 2015-07-17 2017-01-25 株式会社鹭宫制作所 电动阀以及冷冻循环
CN106989193A (zh) * 2016-01-20 2017-07-28 株式会社不二工机 流量调整阀
CN107435753A (zh) * 2016-05-25 2017-12-05 浙江三花智能控制股份有限公司 电子膨胀阀及具有其的制冷设备
CN206338987U (zh) * 2016-11-22 2017-07-18 广东美的暖通设备有限公司 电子膨胀阀和空调系统
CN208794791U (zh) * 2018-04-29 2019-04-26 浙江新劲空调设备有限公司 一种电子膨胀阀

Also Published As

Publication number Publication date
CN113566459A (zh) 2021-10-29

Similar Documents

Publication Publication Date Title
WO2021218804A1 (fr) Vanne d'expansion électronique
KR102408886B1 (ko) 밸브 코어 조립체
US8120454B2 (en) Electromagnetic actuating device
WO2021218845A1 (fr) Vanne de détente électronique
JP2019044880A (ja) 電動弁及び冷凍サイクルシステム
US9631850B2 (en) Thermal expansion valve with one-way control function
WO2020259656A1 (fr) Détendeur électronique
KR20070054265A (ko) 밸브 유지 부재
WO2021218782A1 (fr) Électrovanne d'expansion
JP7478846B2 (ja) 絞り弁及び熱交換システム
WO2017217114A1 (fr) Électro-vanne
CN111102367A (zh) 电子膨胀阀
CN107356024A (zh) 电子膨胀阀
JP5651730B2 (ja) 逆止弁
CN209876100U (zh) 一种电磁膨胀阀
CN217977422U (zh) 截止阀
CN117006290A (zh) 一种静音节流阀及节流阀组件
WO2020083362A1 (fr) Vanne d'expansion électronique
CN210318713U (zh) 一种静音节流阀及节流阀组件
JP4621402B2 (ja) 内燃機関のための燃料噴射弁および該燃料噴射弁を製造する方法
CN220102268U (zh) 阀装置、电子膨胀阀及制冷系统
CN210318565U (zh) 一种降噪节流阀及节流阀组件
JP6964888B2 (ja) 流量調整弁およびその組立方法
CN113062990A (zh) 电子膨胀阀
CN112146313A (zh) 电子膨胀阀

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 21796458

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 21796458

Country of ref document: EP

Kind code of ref document: A1