WO2021218782A1 - 电子膨胀阀 - Google Patents

电子膨胀阀 Download PDF

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Publication number
WO2021218782A1
WO2021218782A1 PCT/CN2021/089109 CN2021089109W WO2021218782A1 WO 2021218782 A1 WO2021218782 A1 WO 2021218782A1 CN 2021089109 W CN2021089109 W CN 2021089109W WO 2021218782 A1 WO2021218782 A1 WO 2021218782A1
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WIPO (PCT)
Prior art keywords
valve
port
diameter
electronic expansion
satisfies
Prior art date
Application number
PCT/CN2021/089109
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English (en)
French (fr)
Inventor
沈自成
何伟鑫
Original Assignee
浙江三花智能控制股份有限公司
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Publication of WO2021218782A1 publication Critical patent/WO2021218782A1/zh

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    • 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
    • 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. Those skilled in the art have been continuously making various attempts to improve the noise problem of electronic expansion valves.
  • 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, and a valve core, 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 port, the electronic expansion valve It includes a first valve cavity and a second valve cavity. The first valve cavity is located on the upper side of the valve port, and the second valve cavity is located on the lower side of the valve port. The electronic expansion valve is located on the valve port.
  • the port is provided with a valve port, 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 interface and the first valve The second interface is in communication with the second valve cavity;
  • the valve core is at least partially located in the first valve chamber, and the valve core and the valve port are matched for adjusting the electronic expansion valve Flow area;
  • the diameter of the valve port is smaller than the diameter of the second port, the diameter of the second port is smaller than the diameter of the second valve cavity;
  • the valve port includes a matching portion and an expansion The mouth portion, the matching portion is closer to the first valve cavity relative to the flaring portion, the flaring portion is closer to the second valve cavity relative to the matching portion, and the height of the matching portion h1 Is smaller than the height h2 of the flaring part, and the value of h1 satisfies: 0.15mm ⁇ h1 ⁇ 0.45mm, the inner diameter of the end of the flaring part close to the first valve cavity is smaller
  • 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 flowing, it flows out to the second valve cavity, which has a relatively large space, and the valve port includes a matching portion and a flaring portion to change the flow space of the refrigerant, thereby improving 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 the valve seat and Part of the valve body, so that the structure of the valve port can be clear
  • Figure 4 is a schematic cross-sectional view of the valve seat component.
  • 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 needle 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 fixedly arranged with the sleeve 16 and or the connecting piece 15 through the metal connecting piece 192
  • 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.
  • 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, so that when the magnetic rotor assembly 17 When rotating, under the action of the thread pair, the screw rod 181 moves up and down relative to the nut assembly 19 while rotating, thereby driving the valve core 182 to move up and down within a certain range.
  • 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 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. 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 fitting portion 1123 and a flaring portion 1124.
  • the fitting portion 1123 can be used to cooperate with the valve needle and change the flow area of the electronic expansion valve as the valve needle 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 connecting line of X2 and X3 and the connecting line of Y2 and Y3 have 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 needle assembly 18, the connector 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 needle and change the flow area of the electronic expansion valve as the valve needle 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 1124a 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 1124a enter the second valve chamber 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 its 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 needle assembly 18, the connector 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 member and the valve seat can be regarded as the indirect abutment between the porous member 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 in a proportionally adjusted 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 inner wall contour of the flared part, the angle of ⁇ meets the condition: 40° ⁇ 80°, and 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.

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Abstract

电子膨胀阀，包括阀座（11）、阀体部件（14）、阀芯（182），阀体部件（14）包括阀体（141），阀体（141）与阀座（11）固定连接；阀座（11）包括阀口部（112），电子膨胀阀包括第一阀腔（A）以及第二阀腔（B），第一阀腔（A）位于阀口部（112）相对上方一侧，第二阀腔（B）位于阀口部（112）相对下方一侧；电子膨胀阀具有第一接口（1211）以及第二接口（1221），阀口（1121）的通径小于第二接口（1221）的通径，第二接口（1221）的通径小于第二阀腔（B）的通径；阀口部（112）包括配合部（1123）和扩口部（1124），配合部（1123）相对于扩口部（1124）更靠近第一阀腔（A），扩口部（1124）相对于配合部（1123）更靠近第二阀腔（B），配合部（1123）的高度h1小于扩口部（1124）的高度h2，且h1的取值满足：0.15mm≤h1≤0.45mm，扩口部（1124）的靠近第一阀腔（A）一端的内径小于扩口部（1124）的靠近第二阀腔（B）一端的内径。

Description

电子膨胀阀
本申请要求：
2020年04月26日提交中国专利局、申请号为202010340951.9、发明名称为“电子膨胀阀”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及制冷控制技术领域，特别涉及电子膨胀阀。
背景技术
制冷系统包括压缩机、节流元件、两个换热器以及其它零部件，节流元件可以采用电子膨胀阀，用于冷媒的节流调节，使用电子膨胀阀可实现相对精确控制而提高系统能效。电子膨胀阀一般包括第一接口和第二接口，冷媒可以从第一接口流入，从第二接口流出，或者从第二接口流入，从第一接口流出。当冷媒经过电子膨胀阀时，可能会产生一定的噪音。改善冷媒通过电子膨胀阀的噪音，是长期以来电子膨胀阀及制冷系统的相关技术人员一直在研究的一个技术课题。本领域技术人员针对电子膨胀阀的噪音问题一直在持续不断地进行各种尝试改进。
发明内容
本发明的目的在于提供一种电子膨胀阀，用于改善冷媒流经电子膨胀阀的噪音问题。
为实现上述目的，本发明的一个实施方式采用如下技术方案：
电子膨胀阀，包括阀座、阀体部件、阀芯，所述阀体部件包括阀体，所述阀体与所述阀座固定连接；所述阀座包括阀口部，所述电子膨胀阀包括第一阀腔以及第二阀腔，所述第一阀腔位于阀口部相对上方一侧，所述第二阀腔位于阀口部相对下方一侧；所述电子膨胀阀在所述阀口部设置有阀口，所述阀口能够连通所述第一阀腔以及第二阀腔；所述电子膨胀阀具有第一接口以及第二接口，所述第一接口与所述第一阀腔连通，所述第二接口与所述第二阀腔连通；所述阀芯至少部分位于所述第一阀腔，所述阀 芯与所述阀口配合用于调节所述电子膨胀阀的通流面积；所述阀口的通径小于所述第二接口的通径，所述第二接口的通径小于所述第二阀腔的通径；所述阀口部包括配合部和扩口部，所述配合部相对于所述扩口部更靠近所述第一阀腔，所述扩口部相对于所述配合部更靠近所述第二阀腔，所述配合部的高度h1小于所述扩口部的高度h2，且h1的取值满足：0.15mm≤h1≤0.45mm，所述扩口部的靠近所述第一阀腔一端的内径小于所述扩口部的靠近所述第二阀腔一端的内径。
上述技术方案通过在电子膨胀阀设置两个阀腔，分别位于阀口部两侧，第一阀腔与第二阀腔能够通过阀口连通，使冷媒在第一流动方向节流时，冷媒节流后流出到第二阀腔，第二阀腔具有相对较大的空间，并且阀口部包括配合部和扩口部，以改变冷媒的流动空间，从而改善冷媒的流动噪音。
附图说明
图1为本申请提供第一种实施例电子膨胀阀的结构示意图；
图2为图1所示电子膨胀阀的I部放大示意图；
图3为图1所示电子膨胀阀包括阀座与阀体部件的局部剖视示意图；
图4为阀座的剖视示意图；
图5为图4的II部放大示意图；
图6为本申请又一种阀座结构的实施例示意图；
图7为本申请提供第二种实施例的电子膨胀阀结构示意图；
图8为第二实施例的阀座部件的剖视示意图；
图9为图7的III部放大示意图；
图10为本申请又一种阀座结构的实施例示意图
图11为本申请提供第三种实施例的电子膨胀阀结构示意图；
图12为图11的IV部放大示意图；
图13为第四实施例的电子膨胀阀阀座结构示意图；
图14为本申请又一种阀座结构的实施例局部剖视图
图15为本申请又一种阀座结构的实施例局部剖视图。
具体实施方式
为了使本领域的技术人员更好的理解本申请提供的技术方案，下面结合附图和具体实施例对本申请的技术方案作进一步的详细说明。
第一实施方式
请参照图1-图4，图1是电子膨胀阀第一种实施例的结构示意图,图2是局部放大示意图,图3是图1电子膨胀阀的局部的剖视示意图,主要包括阀座与阀体部件部分,这样可以清楚阀口部的结构；图4是阀座部件的剖视示意图。
需要指出的是，下面的技术方案针对具体的电子膨胀阀结构进行说明，本申请主要通过对冷媒流动的流道结构进行改进以改善冷媒流动噪音，具体是对阀腔和阀口的结构进行改进。对于电子膨胀阀的其他部件，如磁转子组件、螺母组件、止动装置等部件这里不作限制，本申请的技术方案并不对上述部件的结构进行特别限定，本领域技术人员根据本文披露的技术方案，可以将其应用于所有类似的电子膨胀阀结构。本文关于上述磁转子组件、丝杆阀芯组件等其他部件的描述，仅是便于了解电子膨胀阀的基本工作原理，而并非进行结构上的限定。
电子膨胀阀包括阀座11、阀体部件14，另外还包括连接件15、套管16、磁转子组件17、丝杆阀芯组件18、螺母组件19，阀体部件14包括阀体141，阀座11与阀体141通过焊接固定连接，同时，阀座11固定连接有第一接管121，阀体部件14固定连接有第二接管122。如图1所示的方向，在阀座11的上方一侧，设置有连接件15，连接件15大致呈底部开口的杯型，其底部具有开口，连接件15与阀座11固定连接，同时与套管16固定连接，即阀座通过连接件与套管连接。具体而言，可以在阀座11上侧设置台阶，并将连接件15的底部开口与该台阶配合，并将两者焊接进行固定，或采用其他形式将两者先相对固定如卡接再焊接固定等。
在连接件15的上侧，还设置有套管16，套管16与连接件15可以采用焊接的方式进行固定，这样，套管16、连接件15、阀座11三者固定连接，三者之内的空间，设置有磁转子组件17、丝杆阀芯组件18、螺母组件19。值得注意的是，在上述结构中，连接件15并不是必须存在的，当不存在连接件15时，也可以采用套管16直接与阀座11固定连接的方式，或者采用其他部件固定的方式，比如，直接将阀座11的外缘部向上延伸后与套 管16焊接固定的方式。
磁转子组件17能感应电磁线圈的电磁力而转动，磁转子组件17包括磁转子171以及与磁转子171固定连接或一体设置的连接板172，具体可以将连接板172作为嵌件，注塑成型磁转子171。丝杆阀芯组件18包括丝杆181，丝杆181与连接板172固定连接，这样，丝杆181通过连接板172与磁转子组件17连接成为一个整体，具体的，丝杆181与连接板172可以采用焊接的方式固定连接或者通过卡接、压接等其他固定连接或限位连接方式连接。止动杆173与磁转子组件17固定连接，并大体位于磁转子171所大致围成的区域。
丝杆阀针组件18包括丝杆181、阀芯182、阀芯套183、弹簧184、垫圈部185、挡圈部186、轴套部件187。丝杆181与阀芯182之间通过阀芯套183实现浮动连接，阀芯套183与阀芯182可以通过焊接的方式固定连接，丝杆181的底端固定连接有轴套部件187，两者可以通过焊接的方式固定连接。阀芯182至少有部分位于第一阀腔A(见下文)，在电子膨胀阀工作时，阀芯182能在带动下相对阀口动作一定行程从而与阀口1121配合用于调节流量。即，在电子膨胀阀工作过程中，阀芯182可以相对阀口部112在一定的行程内上下移动以调节阀口1121的开度。在阀芯套183的上端面设置有挡圈部186以及垫圈部185，本实施例中的挡圈部186并不仅限于图示中的C形开口挡圈，也可以采用其它形状的开口挡圈替代；同理，本实施例中的垫圈部185，也不限于图示中的圆环形垫圈，也可采用能起到同样作用的其它挡圈替代，例如也可采用开口挡圈替代。弹簧184外套于丝杆181，具体地，弹簧184的一端与丝杆的上凸缘部1811相抵，弹簧184另一端与垫圈部185相抵，在弹簧184的作用下，垫圈部13与下凸缘部1812相抵。值得说明的是，弹簧14的一端与上凸缘部1811相抵，包括弹簧184的一端与上凸缘部1551直接相抵，也包括弹簧184的一端与上凸缘部1551间接相抵，例如弹簧184与上凸缘部1551之间另行设置有挡圈或者其他部件。轴套部件187的最大外径大于阀芯套183的中心通孔的最小内径，这样，在装配完毕后，阀芯182与丝杆181之间无法脱离，因弹簧184的作用，在阀芯182与阀口部抵接时，阀芯182与丝杆181可以作一定行程的相对运动。本文所述的脱离，是指套筒部183与丝杆181之间 分离成彼此没有任何限制的两个单独部件，而不仅仅指两者没有物理上的接触。
螺母组件19包括螺母191以及连接片192，螺母191与连接片192固定连接，连接片192可以由金属板冲压形成，螺母191通过金属制的连接片192与套管16和或连接件15固定设置，螺母191可以采用非金属材料以连接片192为嵌件经注塑成形，连接片192与连接件15可通过焊接的方式进行固定连接。当不设置连接件时，可以将连接片192与阀座11或套管通过焊接的方式固定连接。
螺母191具有沿其轴向贯通的通孔，螺母在设置该通孔的内侧壁设置内螺纹，与之相应的，丝杆181的外周面设置有相对应的外螺纹，这样当磁转子组件17转动时，丝杆181在螺纹副的作用下，在转动的同时，还相对螺母组件19作升降运动，从而带动阀芯182在一定范围内作升降运动。
螺母191的一部分的外缘部设置有弹簧导轨1911，弹簧导轨1911与螺母191固定连接或限位连接，使得弹簧导轨1911与螺母191在轴向方向和周向方向均实现相对定位，止动杆173随磁转子组件旋转，并带动滑环1912沿着弹簧导轨1911作螺旋滑动，螺母组件上设置有上止动部位和下止动部位，滑环1912能够与上止动部位抵接而停止转动，同时滑环1912能够与下止动部位抵接而停止转动。
电子膨胀阀包括引导部20，引导部20大体呈筒状，在本实施例中，其外周设置有第一外缘部201以及第二外缘部202，其中，第一外缘部201的外径小于第二外缘部202的外径，并且，第一外缘部201的外径与螺母191下端部的内孔相适应，这样，在装配时，螺母191套装在引导部20的上端，第一外缘部201可以对螺母的装配实现导向。第二外缘部202的外径与阀座11的部分内壁的内径相适应，在装配时可以实现导向，具体可以采用过盈压配等方式或者焊接的方式，使引导部20与阀座11固定连接。当然，本领域技术人员可以理解，本实施方式所示的第一外缘部201的外径小于第二外缘部202的外径，是基于阀座内孔的内径小于螺母下端部的内孔的内径设计而确定的，作为等同的替换方式，也可以将阀座内孔的内径设置为大于螺母下端部内孔的内径，或者将两者的内径设置为相同或者大致相同。引导部20的内部还设置有阀芯引导部203，阀芯引导部203与 阀芯182的外径相匹配，使得阀芯182的外缘面可以沿着阀芯引导部203移动，这样，在阀芯移动时，阀芯引导部203能够对阀芯提供良好的导向及径向支撑，可以相对减少因阀芯的摆动而造成阀口部位的异常磨损。需要说明的是，上述第一外缘部201、第二外缘部202、阀芯引导部203均为设置在引导部20表面的某一区域或某一部位，该区域或部位能够实现相应的导向功能，并非对引导部20的形状的限制。实际上引导部20可以根据螺母的尺寸、阀座的尺寸及形状，作出各种不同的适应性改变，只要包括了能对螺母实现导向的第一外缘部201、对阀座实现导向的第二外缘部202、对阀芯实现导向的阀芯引导部203即属于本发明实施例所记载的引导部。
引导部20至少有部分位于第一阀腔A，引导部除了能对阀芯实现导向外，其下端部改变了第一阀腔A的形状，能够对流入第一阀腔A的流体产生一定的影响，有助于进一步降低流体流动的噪音。
电子膨胀阀包括阀座11、阀体部件14、第一接管121、第二接管122，阀座11、阀体部件14、第一接管121、第二接管122通过焊接固定连接，具体地，阀座11与阀体141通过焊接固定连接，阀座11与第一接管121通过焊接固定连接，阀体141与第二接管122通过焊接固定连接。阀座11具有阀口部112，在阀口部112设置有阀口1121，电子膨胀阀具有第一阀腔A以及第二阀腔B，本申请中以阀口部112以上的阀腔、且与第一接管121的第一接口1211连通的部分为第一阀腔A，以阀座以下的阀腔、且与第二接管122的第二接口1221连通的部分为第二阀腔B，第一阀腔A与第二阀腔B能通过阀口1121连通，第一阀腔A位于阀口部112相对上方一侧，第二阀腔B位于阀口部112相对下方一侧，阀口1121的通径D小于第二接口1221的通径H2,第二接口1221的通径H2小于第二阀腔B的通径H1，第一接口1211的通径H3小于第二阀腔B的通径H1。本实施例中第二阀腔B不限于通径大小相同，如通径大小不同，第二阀腔B的通径H1指相对最大处的通径。在本实施方式中，第二阀腔B的通径H1与第一接口1211的通径H3、第二接口1221的通径H2，满足条件：H1≥1.3H3，H1≥1.3H2。
另外阀体141在其侧壁部1411还设置有向内的翻边部1412，以方便 与第二接管122配合连接。阀体141的材料可以采用不锈钢，如阀体由不锈钢板材或管材经拉伸或冲压或挤压加工形成。
有的系统可能需要电子膨胀阀能双向流动，本文中冷媒从第一接口向第二接口方向流动定义为第一流动方向，冷媒从第二接口向第一接口方向流动定义为第二流动方向，或者说冷媒从第一接管经第一阀腔、阀口、第二阀腔向第二接管方向流动定义为第一流动方向，冷媒从第二接管经第二阀腔、阀口、第一阀腔向第一接管方向流动定义为第二流动方向。
本实施例的阀口部112包括配合部1123和扩口部1124，配合部1123可以用于与阀针配合，并随着阀针的升降改变电子膨胀阀的通流面积。配合部1123可以是一个直段部，即沿着中心轴线方向，配合部1123的内径保持不变，这样便于加工，当然，也允许配合部1123设置为内径由上至下逐渐增大或者逐渐减小的锥台状，但一般锥角不超过5°，即配合部1123更接近于一个直段。其中，配合部1123相对于扩口部1124更靠近第一阀腔A，扩口部1124位于配合部1123的下方，且配合部1123和扩口部1124连续设置，可参考图5，图5为本实施方式的阀口部112的剖面视图。沿着中心轴线的由上至下的延伸方向，在阀口部的顶部保持平整状态的情况下，阀口部112的厚度从配合部1123的底部开始径向向外逐渐增大，即阀口部112在配合部1123的部位的壁厚相对最薄，沿着扩口部1124的向下延伸方向逐渐增大。这样，扩口部1124的靠近第一阀腔A一端的内径小于所述扩口部1124的靠近所述第二阀腔B一端的内径。
设配合部1123的高度为h1，扩口部1124的高度为h2，上文所述的阀口部112在配合部的壁厚也可以理解为即配合部1123的高度，阀口部112在扩口部的壁厚也可以理解为扩口部1124的高度，这样，h1＜h2。需要说明的是，本说明书所述的“扩口”是针对阀口部的直径而言，沿着阀口部的中心轴线方向，阀口部的直径呈逐渐增大的趋势。需要说明的是，此处所述的逐渐增大的趋势是指，就阀口部的内径整体而言，靠近第二阀腔B处的内径一般会大于靠近第一阀腔A处的内径，但是，沿着自上而下的方向，允许在其中某一段内径变小，比如设置一条朝向阀口部内壁的凹槽等情况。h1的取值可以是0.15mm-0.45mm之间，甚至在0.25mm-0.35mm之间；h2的取值可以是2.5mm-4.5mm之间，甚至在3.0mm-4mm之间。扩口部1124 在图5所示的纵截面来看，大致呈喇叭状，沿着经过中心轴线的纵截面，扩口部1124的内壁部具有两条轮廓线，两条轮廓线为直线，定义其中一条内壁轮廓线的最高点为X2、最低点为X3，定义另一条内壁轮廓线的最高点为Y2、最低点为Y3，则X2与X3的连接线、Y2与Y3的连接线之间具有角度α，α的取值在40°-80°之间。这样，冷媒在第一流动方向流动时，冷媒经过配合部1123，经喇叭状的扩口部1124，有利于冷媒向周侧区域扩散，从而改善冷媒第一流动方向流动的噪音。即电子膨胀阀在阀口部112的通道空间包括配合部1123与阀芯形成的空间及扩口部1124与阀芯形成的空间，冷媒以第一流动方向流动时，先流经阀口1121，经扩口部1124，再进入第二阀腔B。
在本实施方式中，阀口部112还包括位于扩口部1124下方的凸出部1128以及位于阀口部112的整体的底部的尾部1129，以扩口部1124的锥台状内壁为基准，凸出部1128向中心轴线方向呈凸出状态。尾部1129可以设置为大体与扩口部1124处于同一延伸方向，换言之，可以理解为尾部1129是扩口部1124的延长，而凸出部1128则位于延长的扩口部的内壁，并向中心轴线方向凸出。当然，在图2所示的截面上，尾部1129并非一定在设置为与扩口部1124具有相同的夹角取值，经过申请人试验，尾部1129在该截面的延长线的角度在40°-80°之间即可，仍然能够保证较好的噪音控制效果。
需要说明的是，当h2的取值在2.5mm-4.5mm之间，且α的取值在40°-80°之间时，必然会对阀口部112的直径(或者可大致理解为第二阀腔B的通径)有所要求，而市场上通用的电子膨胀阀，没有设置第二阀腔，仅在阀口部上连接一根普通的接管(内径通常不会超过8mm)，则受限于接管的内径，无法做到同时满足上述h2和α的取值。本实施方式中，由阀体部大致限定的第二阀腔H1的通径取值在9mm-30mm之间，甚至在11mm-14mm之间，在此基础上，可以方便地做到上述h2的取值以及α的取值。
本实施方式提供的阀口部结构，能够在一定程度上降低噪音，特别是第一流动方向的噪音测试结果相对较好，且更优于第二流动方向的噪音测试结果。
作为对上述第一实施方式的局部结构改变，可以改变扩口部1124的轮廓形状，请参照图6，图6是本申请另一种阀座结构的示意图，在此扩展实施例中，扩口部1124不再呈标准的锥面形状，其在纵截面的形状也不呈直线。如图12所示，以扩口部1124的高度为限，位于经过阀座中心轴线的纵截面，扩口部1124具有两条内壁轮廓线，两条轮廓线呈曲线状，图6是对其中一种曲线的示例，实际可以采用各种不同的曲线形状，或者多种曲线形状的组合、曲线和直线的组合等等。定义其中一条内壁轮廓线与配合部1123的交点为X2、最低点为X3，定义另一条内壁轮廓线与配合部1123的交点为Y2、最低点为Y3，则至少存在一个横截面Q1，该横截面Q1与扩口部1124的两条轮内壁轮廓线分别相交于X1、Y1两个点，连接X1和X2得到一条直线，连接Y1和Y2得到另一条直线，两条直线具有θ的角度，θ的角度满足条件：40°≤θ1≤80°。X1到X2在垂直方向的高度h4的取值满足：h4≥2.5mm。这种结构的阀座应用于第一实施方式也能够满足电子膨胀阀对噪音的要求。
第二实施方式
下面结图7-图10，说明本发明的第二实施方式。
请参照图7-图10，其中，图7为本申请提供第二种实施例的电子膨胀阀结构示意图；图8为第二实施例的阀座部件的剖视示意图；图9为图8的III部放大示意图，图10为又一种阀座部件的局部剖视示意图。
为了便于对本实施方式进行描述，特别是体现本实施方式与第一实施方式的不同，对于在技术方案中，与第一实施方式中具有相同的结构及功能的部件，采用同一附图标记，并进行简略描述，着重对于两者的不同点进行详细描述。
与第一实施方式相似，本实施方式的技术方案是对阀腔和阀口的结构进行改进以达到改善噪音的目的。对于电子膨胀阀的其他部件，如磁转子组件、螺母组件、止动装置等部件这里不作限制，本申请的技术方案并不对上述部件的结构进行特别限定，本领域技术人员根据本文披露的技术方案，可以将其应用于所有类似的电子膨胀阀结构。
本实施方式中的磁转子组件17、丝杆阀针组件18、连接件15、套管16、阀体部件14、螺母组件19、引导部20均可以采用与第一实施方式相 同的结构，在此不再赘述。
电子膨胀阀包括阀座11a、阀体部件14、第一接管121、第二接管122，阀座11a、阀体部件14、第一接管121、第二接管122通过焊接固定连接，具体地，阀座11a与阀体141通过焊接固定连接，阀座11a与第一接管121通过焊接固定连接，阀体141与第二接管122通过焊接固定连接。阀座11a具有阀口部112a，在阀口部112a设置有阀口1121a，电子膨胀阀具有第一阀腔A以及第二阀腔B，本申请中以阀口部112a以上的阀腔、且与第一接管121的第一接口1211连通的部分为第一阀腔A，以阀座以下的阀腔、且与第二接管122的第二接口1221连通的部分为第二阀腔B，第一阀腔A与第二阀腔B能通过阀口1121a连通，第一阀腔A位于阀口部112a相对上方一侧，第二阀腔B位于阀口部112a相对下方一侧，阀口1121a的通径D小于第二接口1221的通径H2,第二接口1221的通径H2小于第二阀腔B的通径H1，第一接口1211的通径H3小于第二阀腔B的通径H1。本实施例中第二阀腔B不限于通径大小相同，如通径大小不同，第二阀腔B的通径H1指相对最大处的通径。
本实施例的阀口部112a包括配合部1123a和扩口部1124a，配合部1123a可以用于与阀针配合，并随着阀针的升降改变电子膨胀阀的通流面积。配合部1123a可以是一个直段部，即沿着中心轴线方向，配合部1123a的内径保持不变，这样便于加工，当然，也允许配合部1123a设置为内径由上至下逐渐增大或者逐渐减小的锥台状，但一般锥角不超过5°，即配合部1123更接近于一个直段，下文以配合部1123a呈直线状进行说明。与第一实施方式不同的是，在配合部1123a的上方还设置有过渡部1122a。即过渡部1122a位于阀口部112a的相对顶部，配合部1123a、扩口部1124a依次位于过渡部1122a的下方，阀座11a为一体材料制成。如图8所示，沿着中心轴线的由上至下的延伸方向，阀口部112a的厚度在过渡部1122a逐渐减小，在配合部1123a基本保持不变，在扩口部1124a逐渐增大。此处所述的厚度逐渐增大，是指阀口部112a的厚度从配合部1123a的底部开始径向向外逐渐增大。设配合部1123a的高度为h1，扩口部1124a的高度为h2，过渡部1122a的高度为h3，上文所述阀口部112a在过渡部1122a的厚度也可以理解为过渡部1122a的高度，阀口部112a在配合部1123a的厚度 也可以理解为配合部1123a的高度，阀口112a在扩口部1124a的厚度也可以理解为扩口部1124a的高度。并且满足条件：h3＜h1＜h2。本说明书所述的“扩口”是针对阀口部的直径而言，沿着阀口部的中心轴线方向，从配合部1123a的底部开始，阀口部的直径呈逐渐增大的趋势。此处所述的逐渐增大的趋势是指，就阀口部的内径整体而言，靠近第二阀腔B处的内径一般会大于靠近第一阀腔A处的内径，但是，沿着自上而下的方向，允许在其中某一段内径变小，比如设置一条朝向阀口部内壁的凹槽等情况。
h1的取值可以是0.15mm-0.45mm之间，甚至在0.25mm-0.35mm之间；h2的取值可以是2.5mm-4.5mm之间，甚至在3.0mm-4mm之间；h3的取值可以是0.05mm-0.2mm之间，甚至在0.05mm-0.15mm之间。
扩口部1124a在图9所示的纵截面来看，大致呈喇叭状，且扩口部1124a的内壁部在位于该截面的延长线大至呈一个α的角度，α的取值为锐角，且在40°-80°之间。过渡部1122a由阀口部朝向第一阀腔A倒角而形成，且过渡部1122a与第一阀腔A相邻设置。由于过渡部1122a的高度较小，以放大图来看，截面形状可以是直线状，或者是曲线状。在图8所示的纵截面为例，过渡部呈直线的喇叭状，且过渡部1122a在位于该截面的延长线大至呈一个γ的角度，γ的取值为锐角，且在40°-80°之间。这样，冷媒在第一流动方向流动时，冷媒依次经过过渡部1122a、配合部1123a，经喇叭状的扩口部1124a，有利于冷媒向周侧区域扩散，从而改善冷媒第一流动方向流动的噪音。即电子膨胀阀在阀口部112的通道空间包括过渡部1122a、配合部1123a与阀芯形成的空间及扩口部1124a与阀芯形成的空间，冷媒以第一流动方向流动时，依次流经过渡部1122a、配合部1123a、扩口部1124a，再进入第二阀腔B。
作为对第二实施方式的局部改变，上述过渡部也不仅限于锥台状，即过渡部的纵截面不限于直线。请参照图10，图10是本实施例的另一种阀座结构局部剖视图，过渡部1122a1在纵截面的轮廓线呈曲线状，由于过渡部的高度h5仅在0.05mm-0.2mm之间，将其纵截面的直线改为圆弧状或曲线状的截面，并不会影响本实施例的技术效果。
与第一实施方式相似，当h2的取值在2.5mm-4.5mm之间，且α的取值在40°-80°之间时，必然会对阀口部112a的直径(或者可大致理解为第 二阀腔B的通径)有所要求，而市场上通用的电子膨胀阀，没有设置第二阀腔，仅在阀口部上连接一根普通的接管(内径通常不会超过8mm)，则受限于接管的内径，无法做到同时满足上述h2和α的取值。本实施方式中，由阀体部大致限定的第二阀腔H1的通径取值在9mm-30mm之间，甚至在11mm-14mm之间，在此基础上，可以方便地做到上述h2的取值以及α的取值。
本实施方式提供的阀口部结构，能够在一定程度上降低噪音，特别是第二流动方向的噪音测试结果相对较好，且更优于第一流动方向的噪音测试结果。
第三实施方式
下面结图11-图12，说明本发明的第三实施方式。
请参照图11、图12，其中，图11为本申请提供第三种实施例的电子膨胀阀结构示意图；图12为图11的IV部放大示意图。
为了便于对本实施方式进行描述，特别是体现本实施方式与第一实施方式的不同，对于在技术方案中，与第一实施方式中具有相同的结构及功能的部件，采用同一附图标记，并进行简略描述，着重对于两者的不同点进行详细描述。
与第一实施方式相似，本实施方式的技术方案是对阀腔和阀口的结构进行改进以达到改善噪音的目的。对于电子膨胀阀的其他部件，如磁转子组件、螺母组件、止动装置等部件这里不作限制，本申请的技术方案并不对上述部件的结构进行特别限定，本领域技术人员根据本文披露的技术方案，可以将其应用于所有类似的电子膨胀阀结构。
本实施方式中的磁转子组件17、丝杆阀针组件18、连接件15、套管16、阀体部件14、螺母组件19、引导部20均可以采用与第一实施方式相同的结构，在此不再赘述。
本实施方式的阀座11也采用与第一实施方式相同的结构，包括阀口部112，且阀口部包括配合部1123和扩口部1124。与第一实施方式的差异在于，本实施方式还包括多孔部件21，多孔部件21至少大部分位于第一阀腔A，并且与阀座相对抵接或固定连接。此处所述的抵接，既包括直接抵接，也包括间接抵接，比如在多孔部件与阀座之间增加一个垫片即可视为 多孔部件与阀座间接抵接。多孔部件21呈两端开口状，可以采用金属球经烧结而成，比如使用铜制小球烧结成型，这种结构能够承受一定的压力而不会发生脱落、碎裂、分散等现象。具体在安装时，可以在阀座11的阀口部112的顶部，位于阀口的外侧设置一个环状的安装槽1125，安装时，先将多孔部件21的环状底部对准安装槽1125，然后再将引导部件20装入，通过设置预定的尺寸公差，使引导部件20与多孔部件21相抵接，并对多孔部件21施加一定的压力，从而将多孔部件21固定在阀座11上。当然，此处所述的抵接，也包括直接抵接或间接抵接，比如在多孔部件与引导部件之间增加一个垫片，即可视为多孔部件与引导部件间接抵接。由于安装槽1125的存在，多孔部件21不容易相对阀座发生偏移，从而使结构更加稳定。冷媒从第一接管流入第一阀腔A后，先经过多孔部件21，然后再进入阀口，流入第二阀腔B。
作为在本实施方式中的一个局部替代方案，也可以不在阀口的外侧设置环状的安装槽1125，而是直接将多孔部件21放置在阀口部的顶部，使筒状的部件21的环状底部直接与阀口部的顶部平面相抵接，通过在安装中对多孔部件21施加一定的压力，使多孔部件21发生一定的变形，以保证多孔部件21安装完毕后，在轴向不发生松动。多孔部件21可以采用铜制小球烧结成型，各铜制小球之间存在相对较强的结合力，也能够在发生一定形变的情况下不发生分散或脱落现象。或者，多孔部件21也可以采用不锈钢丝烧结成型，即只要能够形成多孔状的间隙能供冷媒通过即可。
在以上两种安装方式中，安装完毕后，轴向方向以多孔部件21的高度为限，第一阀腔A被多孔部件21分隔，第一阀腔A在多孔部件内部的空间通过阀口1121与第二阀腔A连通，第一阀腔A在多孔部件外部的空间与第一接口1211直接连通，第一接口1211与第二接口通过多孔部件21、阀口1121、第二阀腔B连通。
多孔部件21为铜球绕结成型，冷媒可以穿过多孔部件的各铜球之间形成的间隙，为了减少当杂质过多时将多孔部件堵死的现象，还可以进一步在多孔部件21上开设贯通其筒状壁部的贯通部211，贯通部211将多孔部件的内腔空间与外腔空间连通，这样可以降低多孔部件被杂质堵死的风险。图10所示的是贯通部211的示意图，贯通部211是设置在多孔部件顶端的 若干个缺口，这种结构的好处是，可以在烧结时直接成型，本领域技术人员应当理解，贯通部的具体结构并不局限于图11所示，只要能将多孔部件的壁部贯通即可，比如将贯通部211设置在多孔部件的底部，也可以采用缺口的方式，甚至采用在多孔部件的侧壁打孔的方式等等。
本实施方式提供的阀口部结构，能够在一定程度上降低噪音，并且第一流动方向和第二流动方向的噪音控制效果均相对较好。
上述三种实施方式描述的电子膨胀阀设置有两个阀腔，分别位于阀口部两侧，第一阀腔与第二阀腔能够通过阀口连通，使冷媒在第一流动方向节流时，冷媒节流后流出到第二阀腔，第二阀腔具有相对较大的空间，结合阀口部或者阀口部与多孔部件结合的设置，改变冷媒的流动方式和流动空间，从而改善冷媒的流动噪音。
上述各实施例描述的阀体，可以采用不锈钢材料经拉伸或挤压等加工形成，如采用板材或管材加工形成，这样可以使加工相对方便,并使阀体的壁厚小于1mm。本文中提及的通径，指其截面不限于是圆形的，如阀口的截面不限于圆形，还可以包括其他形状，如第二阀腔的通径，其截面也不限于圆形。第二接口的通径H2大于阀口1121的通径D，第二阀腔B的通径H1大于第二接管连通的第二接口的通径H2，第二阀腔B的通径H1大于第一接管用于连通的第一接口的通径H3，第二接管连通的第二接口的通径H2大于阀口1121的通径D。这里，通径相当于当量内径，即以该处的截面积转变为相同截面积的圆形时的内径值，或者说两者具有相同的截面积，这样具有相同的通流面积。阀体具有底壁部1413，底壁部1413到阀口部的距离L是第二接管122的通径H2的两倍以上，即第二阀腔B具有足够的高度，能够对流体噪音的减少具有一定的作用。
另外，作为另一种具体的实施方式，阀芯182包括调节部1821以及尖状部1822，调节部1821和尖状部1822大致位于阀芯182的底端，其中，尖状部1822位于调节部1821的下方。调节部1821的截面轮廓线大致呈平滑过渡的曲线状。阀芯182与阀口部112抵接而处于关阀状态时，调节部1821的外缘部与阀口部112接触，当电子膨胀阀开阀时，丝杆带动阀芯182上移，此时，调节部1821的外缘与阀口部112之间形成环状的间隙以供冷 媒通过，并且，随着阀芯182的逐渐上移，由于调节部1821的截面轮廓线呈平滑过渡的曲线，上述的环状间隙也会随之改变大小，并且流量大致呈等比例调节状态，以区别于本领域常用的锥台状阀芯的线性调节状态。需要说明的是，调节部的截面轮廓线可以是多条曲线组合而成。在调节部1821的底部设置有一体结构的尖状部1822，尖状部1822整体从调节部1821的底部向下凸出。尖状部1822改变了阀芯182与阀口部112之间所形成的环状间隙形状，相对于不设置尖状部的阀芯而言，能够填充一部分冷媒流通路径，减少冷媒在阀芯底部有可能出现涡流的可能性，有助于降低冷媒流动的噪音。需要说明的是，阀芯的结构可以应用至上述任一实施方式中，即包括调节部和尖状部的阀芯结构应用于任一实施方式的阀口部结构，以获得更好的噪音控制效果。
作为又一种具体的实施方式，还可以在上述三种实施例的基础上，对其中的阀座部件的结构进行进一步的改变，特别是对于阀口部的形状。请参照图13，图13是本发明第四实施方式的电子膨胀阀阀座结构示意图。需要说明的是，本实施方式是在第一实施方式的基础上改进而成，作为一个完整的实施方式，只需将图11所示的阀座部件替换第一实施方式的图1所示的阀座部件即可形成。为了使说明书不过于冗长，在本实施例中不再对除了阀座部件之外的其他电子膨胀阀零部件进行说明。同时，需要说明的是，本实施方式的阀座部件完全可以应用于第二实施方式或者第三实施方式，本领域技术人员可以理解，只需要将第二实施方式或者第三实施方式的技术方案中的阀座部件替换为本实施方式记载的阀座部件即可。因此，这些简单的排列组合所形成的新的技术方案也显然应当属于本发明的保护范围。
如图13所示，本实施例的阀座11b包括阀口部112b，阀口部112b包括配合部1121b和扩口部1122b，与第一实施方式不同的是，扩口部1122b一直延伸至阀口部112b的底端。如图13所示，沿着中心轴线的由上至下的延伸方向，阀口部112b的厚度在扩口部1122b逐渐增大。此处所述的厚度逐渐增大，是指阀口部112b的厚度从配合部1121b的底部开始径向向外逐渐增大。设配合部1121b的高度为h1，扩口部1122b的高度为h2，阀口部112b在配合部1121b的厚度也可以理解为配合部1121b的高度，阀口 112b在扩口部1122b的厚度也可以理解为扩口部1122b的高度。并且满足条件：h1＜h2。本说明书所述的“扩口”是针对阀口部的直径而言，沿着阀口部的中心轴线方向，从配合部1122b的底部开始，阀口部的直径呈逐渐增大的趋势。
h1的取值可以是0.15mm-0.45mm之间，甚至在0.25mm-0.35mm之间；h2的取值可以是4.5mm-6.5mm之间，甚至在5.0mm-6mm之间。扩口部1122b在图13所示的纵截面来看，大致呈喇叭状，沿着阀口部112b的经过中心轴线的纵截面，扩口部1122b的内壁部具有两条轮廓线，两条轮廓线为直线，定义其中一条内壁轮廓线与配合部的交点为X2、最低点为X3，定义另一条内壁轮廓线与配合部的交点为Y2、最低点为Y3，则X2与X3的连接线、Y2与Y3的连接线之间具有角度α，所述角度α的取值满足：40°≤α≤80°。需要说明的是，当h2的取值在4.5mm-6.5mm之间，且α的取值在40°-80°之间时，必然会对阀口部112b的直径(或者可大致理解为第二阀腔B的通径)有所要求，而市场上通用的电子膨胀阀，没有设置第二阀腔，仅在阀口部上连接一根普通的接管(内径通常不会超过8mm)，则受限于接管的内径，无法做到同时满足上述h2和α的取值。本实施方式中，由阀体部大致限定的第二阀腔H1的通径取值在9mm-30mm之间，甚至在11mm-14mm之间，在此基础上，可以方便地做到h2的取值以及α的取值。
这样，冷媒在第一流动方向流动时，冷媒依次经过配合部1121b，经喇叭状的扩口部1122b，有利于冷媒向周侧区域扩散，从而改善冷媒第一流动方向流动的噪音。即电子膨胀阀在阀口部112的通道空间包括配合部1121b与阀芯形成的空间及扩口部1122b与阀芯形成的空间，冷媒以第一流动方向流动时，依次流经配合部1121b、扩口部1122b，再进入第二阀腔B。
相对于本实施例的扩口部1122b，可以将第一实施方式、第二实施方式、第三实施方式记载的配合部理解为本实施方式的配合部，可以将第一实施方式、第二实施方式、第三实施方式记载的扩口部理解为本实施方式的扩口部1122b的一部分。在阀口部112b不设置凸出部的情况下，本实施例的阀座部件应用于电子膨胀阀时，经试验验证，不会导致噪音效果变差。
作为对第四实施方式的局部结构改变，可以改变扩口部1122b的轮廓 形状，请参照图14，图14是本申请另一种阀座结构的示意图，在此扩展实施例中，扩口部1122b不再呈标准的锥面形状，其在纵截面的形状也不呈直线。如图14所示，位于图示阀座的经过中心轴线的纵横面，扩口部1122b的内壁的轮廓线呈不规则的曲线状，在该纵截面，扩口部1122b具有两条内壁轮廓线，定义其中一条轮廓线与配合部的交点为X2、最低点为X3，定义其中另一条轮廓线与配合部的交点为Y2、最低点为Y3，以扩口部1122b的高度为限，至少存在一个横截面Q1，该横截面Q1与扩口部1122b的内壁的轮廓线相交于X1、Y2两个交点，连接X1和X2得到一条直线，连接Y1和Y2得到另一条直线，两条直线具有θ的角度，θ的角度满足条件：40°≤θ≤80°。X1到X2在垂直方向的高度h4的取值满足：h4≥2.5mm。这种结构的阀座应用于第一实施方式或者第二实施方式也能够满足电子膨胀阀对噪音的要求，限于篇幅，不再对本实施例的阀座应用于第二实施方式进行详细描述，即相当于在本实施的阀座上增加一个过渡部即可。需要说明的是，沿着阀口部的中心轴线方向，阀口部的直径呈逐渐增大的趋势，此处所述的逐渐增大的趋势是指，就阀口部的内径整体而言，靠近第二阀腔B处的内径一般会大于靠近第一阀腔A处的内径，但是，沿着自上而下的方向，允许在其中某一段内径变小，比如设置一条朝向阀口部内壁的凹槽等情况。
请参照图15，图15为本申请又一种阀座结构的实施例局部剖视图。在此扩展实施例中，位于图示阀座的经过中心轴线的纵横面，扩口部1122b的内壁的轮廓线呈连续的弧线状，在该纵截面，扩口部1122b具有两条内壁轮廓线，定义其中一条轮廓线与配合部的交点为X2、最低点为X3，定义其中另一条轮廓线与配合部的交点为Y2、最低点为Y3，以扩口部1122b的高度为限，至少存在一个横截面Q1，该横截面Q1与扩口部1122b的内壁的轮廓线相交于X1、Y2两个交点，连接X1和X2得到一条直线，连接Y1和Y2得到另一条直线，两条直线具有θ的角度，θ的角度满足条件：40°≤θ≤80°。X1到X2在垂直方向的高度h4的取值满足：h4≥2.5mm。而此时，扩口部的内壁轮廓线X2和X3的连线、Y2和Y3的连线具有α的角度，此时的X3、Y3相对更靠近阀座的外侧壁，α的角度会大于80°，但由于在扩口部的内壁轮廓线上存在X1、Y1，使得θ的角度满足条件： 40°≤θ≤80°，并且满足h4≥2.5mm，仍然具有降低噪音的效果。
这种结构的阀座应用于第一实施方式或者第二实施方式也能够满足电子膨胀阀对噪音的要求，限于篇幅，不再对本实施例的阀座应用于第二实施方式进行详细描述，即相当于在本实施的阀座上增加一个过渡部即可。需要说明的是，沿着阀口部的中心轴线方向，阀口部的直径呈逐渐增大的趋势，此处所述的逐渐增大的趋势是指，就阀口部的内径整体而言，靠近第二阀腔B处的内径一般会大于靠近第一阀腔A处的内径，但是，沿着自上而下的方向，允许在其中某一段内径变小，比如设置一条朝向阀口部内壁的凹槽等情况。
以上各实施方式中所记载的技术特征，在不发生冲突的基础上，可以互相进行排列组合，从而形成更多的实施例，限于篇幅，申请人不再一一罗列所有的排列组合方式，本领域技术人员应当理解，在不需要付出创造性劳动的情况下，这些简单的组合显然也属于本发明的保护范围。
需要说明的是，本文所提及的上、下、左、右等方位名词，均是以说明书附图作为基准，为便于描述而引入的；以及部件名称中的“第一”、“第二”等序数词，也是为了便于描述而引入的，并不意味着对部件的任何次序作出任何的限定，另外，由于上述实施例所提供的各零部件之间的某些部位的功能相同，故本说明书对这些部位采用统一命名的方式。以上对相关技术方案所提供的电子膨胀阀进行了详细介绍，本文中应用了具体实施例进行了阐述，以上实施例的说明只是用于帮助理解本发明的方法及其核心思想，并非对本发明作任何形式上的限制。

Claims (9)

  1. 一种电子膨胀阀，包括阀座、阀体部件、阀芯，所述阀体部件包括阀体，所述阀体与所述阀座固定连接；所述阀座包括阀口部，所述电子膨胀阀包括第一阀腔(A)以及第二阀腔(B)，所述第一阀腔(A)位于阀口部(112)相对上方一侧，所述第二阀腔(B)位于阀口部相对下方一侧；所述电子膨胀阀在所述阀口部设置有阀口(1121)，所述阀口(1121)能够连通所述第一阀腔(A)以及第二阀腔(B)；所述电子膨胀阀具有第一接口(1211)以及第二接口(1221)，所述第一接口(1211)与所述第一阀腔(A)连通，所述第二接口(1221)与所述第二阀腔(B)连通；所述阀芯至少部分位于所述第一阀腔(A)，所述阀芯与所述阀口(1121)配合用于调节所述电子膨胀阀的通流面积；所述阀口(1121)的通径小于所述第二接口(1221)的通径，所述第二接口(1221)的通径小于所述第二阀腔(B)的通径；
    所述阀口部(112)包括配合部(1123)和扩口部(1124)，所述配合部(1123)相对于所述扩口部(1124)更靠近所述第一阀腔(A)，所述扩口部(1124)相对于所述配合部(1123)更靠近所述第二阀腔(B)，所述配合部(1123)的高度h1小于所述扩口部(1124)的高度h2，且h1的取值满足：0.15mm≤h1≤0.45mm，所述扩口部(1124)的靠近所述第一阀腔(A)一端的内径小于所述扩口部(1124)的靠近所述第二阀腔(B)一端的内径。
  2. 如权利要求1所述的电子膨胀阀，其特征在于，以所述扩口部(1124)的高度为限，位于经过所述阀座(11)中心轴线的纵截面，所述扩口部(1124)具有两条内壁轮廓线，定义其中一条内壁轮廓线与所述配合部的交点为X2，定义另一条内壁轮廓线与所述配合部的交点为Y2，所述扩口部(1124)至少存在一个横截面Q1，所述横截面Q1与所述扩口部(1124)的两条内壁轮廓线分别相交于X1、Y1，则X1与X2的连接线、Y1与Y2的连接线之间具有角度θ，θ的取值满足：40°≤θ≤80°，所述X1到X2的高度h4的取值满足：h4≥2.5mm。
  3. 如权利要求2所述的电子膨胀阀，其特征在于，所述h1的取值满足：0.25mm≤h1≤0.35mm，h2的取值满足：2.5mm≤h2≤6.5mm，所述第二阀腔(B)的通径H1满足：9mm≤H1≤30mm。
  4. 如权利要求3所述的电子膨胀阀，其特征在于，沿着所述阀口部(112)的经过中心轴线的纵截面，所述扩口部(1124)的内壁部具有两条轮廓线，所述两条轮廓线为直线，定义其中一条内壁轮廓线的最低点为X3，定义另一条内壁轮廓线的最低点为Y3，则X2与X3的连接线、Y2与Y3的连接线之间具有角度α，所述角度α的取值满足：40°≤α≤80°。
  5. 如权利要求4所述的电子膨胀阀，其特征在于，所述阀口部(112)还包括凸出部(1128)和尾部(1129)，所述凸出部(1128)朝向所述阀口部(112)的中心轴线方向凸出，所述凸出部(1128)和所述尾部(1129)相对于所述配合部(1123)更靠近所述第二阀腔(B)，所述角度α的取值满足：50°≤α≤70°。
  6. 如权利要求2所述的电子膨胀阀，其特征在于，所述扩口部延伸至所述阀口部的底端，所述配合部的高度h1小于所述扩口部的高度h2，所述h1的取值满足：0.25mm≤h1≤0.35mm，h2的取值满足：4.5mm≤h2≤6.5mm，所述第二阀腔(B)的通径H1满足：9mm≤H1≤30mm。
  7. 如权利要求6所述的电子膨胀阀，其特征在于，所述扩口部的高度h2满足：5.0mm≤h7≤6mm，所述第二阀腔(B)的通径H1满足：11mm≤H1≤14mm。
  8. 如权利要求7所述的电子膨胀阀，其特征在于，沿着所述阀口部(112)的经过中心轴线的纵截面，所述扩口部的内壁部具有两条轮廓线，所述两条轮廓线为直线，定义其中一条内壁轮廓线的最低点为X3，定义另一条内壁轮廓线的最低点为Y3，则X2与X3的连接线、Y2与Y3的连接线之间具有角度α，所述角度α的取值满足：40°≤α≤80°。
  9. 如权利要求1-8任一项所述的电子膨胀阀，其特征在于，所述第二阀腔(B)的通径H1与所述第一接口(1211)的通径H3、所述第二接口(1221)的通径H2，满足条件：H1≥1.3H3，H1≥1.3H2。
PCT/CN2021/089109 2020-04-26 2021-04-23 电子膨胀阀 WO2021218782A1 (zh)

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