WO2013177865A1 - 一种电子膨胀阀 - Google Patents

一种电子膨胀阀 Download PDF

Info

Publication number
WO2013177865A1
WO2013177865A1 PCT/CN2012/079932 CN2012079932W WO2013177865A1 WO 2013177865 A1 WO2013177865 A1 WO 2013177865A1 CN 2012079932 W CN2012079932 W CN 2012079932W WO 2013177865 A1 WO2013177865 A1 WO 2013177865A1
Authority
WO
WIPO (PCT)
Prior art keywords
seat
valve
spool
sleeve
hole
Prior art date
Application number
PCT/CN2012/079932
Other languages
English (en)
French (fr)
Inventor
詹才意
袁泽
Original Assignee
浙江三花股份有限公司
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 浙江三花股份有限公司 filed Critical 浙江三花股份有限公司
Priority to US14/401,484 priority Critical patent/US9341399B2/en
Publication of WO2013177865A1 publication Critical patent/WO2013177865A1/zh

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • 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
    • 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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
    • F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
    • F16K3/246—Combination of a sliding valve and a lift valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/08—Means in valves for absorbing fluid energy for decreasing pressure or noise level and having a throttling member separate from the closure member, e.g. screens, slots, labyrinths
    • 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
    • F25B41/38—Expansion means; Dispositions thereof specially adapted for reversible cycles, e.g. bidirectional expansion restrictors
    • 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
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87917—Flow path with serial valves and/or closures
    • Y10T137/88022—One valve head provides seat for other head

Definitions

  • the invention relates to the technical field of fluid control components, and in particular to an electronic expansion valve. Background technique
  • the high-temperature and high-pressure gaseous refrigerant from the exhaust pipe of the compressor 7'8 passes through the D-connector of the four-way valve 7 ⁇ , the E-connector, the outdoor exchanger 7'2 (condensation heat release), and the first check valve 7 '4 (the first electronic expansion valve 7'3 does not adjust), the second electronic expansion valve 7'5 (when the second check valve 7'6 is closed, the second electronic expansion valve 7'5 acts as a flow regulator ), eventually entering the indoor exchanger 77 to evaporate and absorb heat for cooling.
  • the second electronic expansion valve 7'6 is closer to the indoor exchanger 77, heat loss can be reduced (if the electronic expansion valve is too far from the evaporator, the low-temperature low-pressure liquid refrigerant from the electronic expansion valve is easily gas-filled. It not only causes heat loss, but also greatly reduces the utilization rate of the evaporator).
  • the medium-temperature and high-pressure refrigerant from the outdoor heat exchanger 7'2 passes through the first electronic expansion valve 7'3, even if the expansion valve is fully opened, the throttling effect will occur, and the cooling is reduced.
  • the pressure of the agent is transferred to the second electronic expansion valve 7'5, the refrigerant is likely to partially vaporize, affecting the throttling effect of the electronic expansion valve and reducing the system efficiency.
  • the high-temperature and high-pressure gaseous refrigerant from the compressor 7'8 exhaust pipe passes through the D-connector of the four-way valve 7 ⁇ , the C-connector, the indoor exchanger 77 (condensation heat release), and the second check valve 7' 6 (the second electronic expansion valve 7'5 does not adjust), the first electronic expansion valve 7'3 (at this time, the first check valve 7'4 is closed, and the first electronic expansion valve 7'3 is used for flow regulation) Finally, enter the outdoor exchanger 7'2 to evaporate and absorb heat for cooling.
  • the first electronic expansion valve 7'3 is closer to the outdoor exchanger 7'2
  • the heat loss can be reduced (if the electronic expansion valve is too far from the evaporator, the low-temperature low-pressure liquid refrigerant coming out of the electronic expansion valve is easily vaporized, which not only causes heat loss, but also greatly reduces the evaporator utilization).
  • the medium-temperature and high-pressure refrigerant from the indoor heat exchanger 77 passes through the second electronic expansion valve 7'5, even if the expansion valve is fully opened, the throttling effect will occur, and the refrigerant is lowered.
  • the pressure, when the first electronic expansion valve 7'3 flows, will partially vaporize the refrigerant, affecting the throttling effect of the electronic expansion valve and reducing the system efficiency.
  • Japanese Patent Laid-Open No. 2009-287913 discloses an electronic expansion valve with a check valve function. Specifically, please refer to FIG. 2 and FIG. 3, FIG. The schematic diagram of the electronic expansion valve in the prior art when the flow rate is adjusted, and FIG. 3 is a schematic structural view of the prior art electronic expansion valve in the reverse conduction direction.
  • the prior art electronic expansion valve includes a valve seat 1'.
  • the valve seat 1' is provided with a main valve chamber 1'1, a horizontal interface portion ⁇ 2, and a vertical interface portion ⁇ 3.
  • the upper end opening of the portion 3 forms a main valve port ⁇ 31;
  • the main valve chamber 1 ⁇ is provided with a valve core seat 2 ′, and the valve core seat 2 ′ is guided by the circumferential side wall thereof to the circumferential inner side wall of the main valve chamber 1 ,. So that it can reciprocate in the axial direction of the main valve chamber 1 ⁇ , thereby opening and closing the main valve port 1'31;
  • the valve core seat 2' is provided with a sub-valve chamber 2 ⁇ , a spool
  • the seat 2' is provided with a spool valve port 2'2 communicating with the auxiliary valve chamber 2, the valve needle member
  • valve 3' extends into the secondary valve chamber 2 ⁇ and reciprocates in the axial direction to open and close the spool valve port 2'2; further, as shown in Figures 2 and 3, the circumferential direction of the valve core seat 2' A through hole 2'3 communicating with the sub valve chamber 2B is also formed in the side wall, and the through hole 2'3 faces the horizontal interface portion ⁇ 2 and communicates with the sub valve chamber 2 and the horizontal interface portion 1'2.
  • the horizontal joint portion 1'2 is connected to the cross pipe 4'
  • the vertical joint portion 1'3 is connected to the vertical pipe 4'2
  • the refrigerant fluid flows from the cross pipe 4 to the vertical pipe 4'2.
  • the horizontal interface part 1 '2 the side is the high pressure area
  • the vertical interface part ⁇ 3 the side is the low pressure area
  • the refrigerant fluid flows from the vertical connection pipe 1′3 to the transverse connection pipe 1′2 (also That is, the vertical interface portion 1'3 - the side is the high pressure region, and the lateral interface portion 1 '2 - the side is the low pressure region) is positioned to flow in the reverse direction.
  • the needle member 3' is connected to the lead screw 5', and the screw rod 5'' is screwed to the nut 5'2; in this configuration, under the action of the magnetic field of the coil 6, the magnet 6'2 rotates, the screw rod 5 turns and the nut 5'2 thread fit thus along the shaft The reciprocating motion causes the valve needle member 3' to reciprocate in the axial direction to open or close the spool valve port 2'2.
  • the spool seat 2′ moves downward. , thereby closing the main valve port 1'31; on this basis, the refrigerant enters the sub-valve chamber 2 ⁇ through the through-hole 2'3 through the transverse port portion 1'2, and the valve needle member 3' opens the spool valve port 2'2, The refrigerant entering the secondary valve chamber 2 ⁇ flows from the spool valve port 2'2 to the vertical port portion 1'3, and then flows into the vertical pipe 4'2.
  • the axial movement of the screw rod 5 allows the valve needle member 3' to adjust the opening degree of the spool valve port 2'2, thereby achieving the purpose of adjusting the flow rate of the electronic expansion valve.
  • the technical problem to be solved by the present invention is to provide an electronic expansion valve.
  • the structural design of the electronic expansion valve can prevent the high pressure refrigerant from causing excessive impact on the valve core seat, preventing eccentricity thereof, thereby avoiding internal
  • the occurrence of leakage ensures the reliability of the work of the system.
  • the present invention provides an electronic expansion valve including a valve seat, a vertical pipe and a cross pipe, the valve seat is provided with a main valve cavity; the electronic expansion valve further includes a main body communicating with the vertical pipe a valve port and a spool seat that can open and close the main valve port, the valve core seat is provided with a spool valve port connectable with the vertical pipe, and the electronic expansion valve further comprises a valve core that can be opened and closed a valve needle member of the valve port; the electronic expansion valve further includes a drive member that drives axial movement of the valve needle member,
  • the driving component includes a screw rod and a nut threadedly engaged with the screw rod;
  • the spool seat closes the main valve port, and the refrigerant flows to the vertical pipe via the spool valve port, and the valve needle member adjusts the opening of the spool valve port under the driving of the driving member
  • the spool seat moves up to open the main valve port, and the refrigerant flows to the cross pipe through the main valve port;
  • a sleeve is fixed in the main valve chamber, the spool seat is movably disposed in the sleeve in the axial direction, and a lower portion of the valve needle member extends into the sleeve to open and close the spool Valve port
  • a circumferential flow wall of the sleeve is provided with a sleeve flow passage connecting the inner cavity and the main valve cavity;
  • the wide core seat is provided with a wide core through hole communicating with the vertical pipe, and the The upper end opening of the wide core through hole forms the spool valve port,
  • the circumferential side wall of the valve core seat is provided with a spool seat side ⁇ L communicating with the spool seat through hole;
  • the spool seat closes the main valve port to interrupt the communication between the sleeve flow passage and the side hole of the spool seat, and the refrigerant flows to the spool valve port through the sleeve flow passage;
  • the spool seat moves up to open the main valve port and communicates with the spool seat side hole and the sleeve flow passage.
  • the lower end of the sleeve is supported by the valve seat, and the inner wall of the lower end portion of the sleeve forms a spool seat guide hole, and the upper port of the spool seat guide hole forms the main valve port.
  • valve seat is provided with a vertical interface portion, and the lower end portion of the sleeve is extended by the vertical mouth portion and supported by the inner wall of the vertical interface portion;
  • the riser tube is further mounted on a circumferential outer side wall of the lower end of the sleeve.
  • a circumferential outer side wall of the valve core seat is provided with a spool outer guiding portion that is fitted into the valve core seat guiding hole, and a top end of the outer portion of the valve core seat protrudes outward to form an opening and The spool seat seal of the main valve port is closed.
  • the wide core through hole includes a first axial hole communicating with the vertical pipe, and a second axial hole disposed above the first axial hole, and an upper end hole of the second axial hole
  • the mouth forms a wide opening of the valve core; and the flow area of the first axial hole is larger than the flow area of the second axial hole.
  • valve core seat side hole is formed on a circumferential side wall of the valve core seat where the first axial hole is located, and communicates with the first axial hole; and, the wide core seat side hole total The flow area is larger than the flow area of the first axial hole.
  • the first axial hole and the second axial hole are further communicated through the tapered hole.
  • the sleeve is a unitary structure, and the sleeve flow passage is a plurality of through holes formed in the circumferential side wall of the sleeve.
  • the upper portion of the sleeve is provided with a nut inner guiding hole, and the sleeve is fitted with the inner guiding hole of the nut to the circumferential outer wall of the lower portion of the nut.
  • the sleeve is a split structure, comprising a nut guide seat fixed to an inner side wall of the valve seat, and a spool seat fitting portion supported by a bottom wall of the valve seat; the nut guide seat and the valve
  • the gap of the core seat mating portion in the axial direction of the valve seat forms the sleeve flow path.
  • the nut guiding seat is provided with a guiding inner hole, and a lower portion of the nut is guided to fit in the guiding inner hole.
  • the side wall of the guiding seat is provided with a circumferential protruding portion fitted on the inner side wall of the valve seat, and the circumferential protruding portion is provided with a plurality of communicating the upper cavity and the lower cavity The gap.
  • the reciprocating stroke of the spool seat is smaller than the reciprocating stroke of the valve needle member such that the spool seat is moved up and the upper end surface thereof is abutted against the lower end surface of the nut.
  • a sleeve is fixed in the main valve cavity of the electronic expansion valve provided by the present invention, and the valve core seat is movably disposed in the sleeve in the axial direction, and the valve needle component is a lower portion extending into the sleeve to open and close the spool valve port;
  • a circumferential flow wall of the sleeve is provided with a sleeve flow passage connecting the inner cavity and the main valve cavity;
  • the seat is provided with a spool seat through hole communicating with the vertical pipe, and the upper end opening of the spool seat through hole forms the spool valve port, and the circumferential side wall of the valve core seat is opened and a spool seat side hole communicating with the through hole of the spool seat; when the refrigerant flows in the forward direction, the spool seat closes the main valve port to interrupt the communication between the sleeve flow passage and the side hole of the spool seat, and the refrigerant passes through the The
  • the side of the cross pipe When the refrigerant is flowing forward, the side of the cross pipe is a high pressure zone, and the side of the pipe is a low pressure zone. Under the action of the pressure difference of the refrigerant, the spool seat moves downward to close the main valve port; on this basis, the refrigerant passes through the sleeve.
  • the barrel flow path enters the inner cavity of the sleeve.
  • the valve needle member opens the valve port of the valve core, the refrigerant enters the side of the vertical connection tube through the valve port of the valve core. In the process, the valve needle member can follow the axial direction of the screw rod. The reciprocating motion adjusts the opening of the spool valve port to achieve the purpose of adjusting the flow rate of the electronic expansion valve.
  • one side of the vertical pipe is a high pressure zone, and one side of the pipe is a low pressure zone.
  • the spool seat moves upward, thereby opening the main valve port to realize the sleeve flow path.
  • the refrigerant flows into the main valve chamber through the spool seat through hole, the spool seat side hole, the main valve port and the sleeve flow passage, and finally enters the side of the cross pipe, thereby realizing the one-way valve single guide The purpose of the pass.
  • the electronic expansion valve provided by the invention can prevent the high pressure refrigerant from causing excessive impact on the valve core seat and prevent eccentricity, thereby avoiding the occurrence of internal leakage and ensuring the reliability of the operation of the system.
  • FIG. 1 is a schematic view showing the working principle of an air conditioning refrigeration system in the prior art
  • FIG. 2 is a schematic structural view of a prior art electronic expansion valve when the flow rate is adjusted
  • FIG. 3 is a schematic structural view of the prior art electronic expansion valve when the reverse flow is performed
  • Figure 4 is a schematic view showing the structure of the electronic expansion valve in the forward flow of the refrigerant in the first embodiment of the present invention
  • FIG. 5 is a schematic structural view of the electronic expansion valve of FIG. 4 when the refrigerant flows in the reverse direction;
  • FIG. 6 is a schematic structural view of the sleeve of the electronic expansion valve of FIG. 4;
  • Figure 7 is a schematic structural view of a valve core seat of the electronic expansion valve of Figure 4.
  • Figure 8 is a schematic view showing the structure of an electronic expansion valve in a forward flow of a refrigerant in a second embodiment of the present invention.
  • FIG. 9 is a schematic structural view of the electronic expansion valve of FIG. 8 when the refrigerant flows in the opposite direction;
  • FIG. 10 is a structural schematic view of the valve body seat fitting portion of the sleeve of the electronic expansion valve of FIG. 8;
  • FIG. 11 is an electronic expansion valve of FIG. Schematic diagram of the nut guide seat of the sleeve;
  • FIG. 12 and FIG. 4 and FIG. 8 are structural diagrams of the nut of the electronic expansion valve.
  • ⁇ Valve seat 1 ⁇ Main valve cavity; ⁇ 2 transverse interface part; ⁇ 3 vertical interface part; ⁇ 31 main valve port; 2' spool seat; 2 ⁇ Sewer valve cavity; 2'2 spool valve port; 2'3 through hole; 3' valve needle component;
  • valve seat 11 main valve cavity; 12 horizontal interface; 13 vertical interface;
  • the core of the invention provides an electronic expansion valve.
  • the structure of the electronic expansion valve can prevent the high pressure refrigerant from causing excessive impact on the valve core seat, preventing eccentricity, thereby avoiding the occurrence of internal leakage. , to ensure the reliability of the work of the system.
  • FIG. 4 is a schematic structural view of the electronic expansion valve in the forward flow of the refrigerant in the first embodiment of the present invention
  • FIG. 5 is the refrigerant in the electronic expansion valve of FIG.
  • FIG. 6 is a structural schematic view of the sleeve of the electronic expansion valve of FIG. 4
  • FIG. 7 is a schematic structural view of the valve core seat of the electronic expansion valve of FIG.
  • the electronic expansion valve provided by the present invention
  • the valve seat 1 is provided, the valve seat 1 is provided with a main valve chamber 11, a horizontal interface portion 12 and a vertical interface portion 13, the horizontal interface portion 12 is mounted with a transverse tube 52, and the vertical interface portion 13 is mounted with a vertical connection tube 51;
  • the electronic expansion valve further includes a main valve port 441 communicating with the vertical pipe 51 and a valve core seat 2 for opening and closing the main valve port 441, the valve core seat 2 is provided with a spool valve port 21 connectable with the vertical pipe 51, and the electronic expansion valve further includes
  • the valve needle member 3 of the spool valve port 21 can be opened and closed;
  • the electronic expansion valve further includes a driving member that drives the axial movement of the valve needle member 3, the driving member including a screw rod 61 and a nut threadedly engaged with the screw rod 61 62.
  • the spool seat 2 closes the main valve port 441, the refrigerant flows to the vertical pipe 51 via the spool valve port 21, and the valve needle member 3 is actuated by the driving member.
  • the opening degree of the core valve port 21 when the refrigerant moves in the reverse direction, the spool seat 2 moves up to open the main valve port 441, and the refrigerant flows to the cross pipe 52 via the main valve port 441.
  • a sleeve 4 is fixed in the main valve chamber 11, and the spool seat 2 is movably disposed in the sleeve 4 in the axial direction, and the lower portion of the needle member 3 is extended.
  • the spool valve port 21 is opened and closed in the sleeve 4; as shown in Fig.
  • the circumferential side wall of the sleeve 4 is provided with a sleeve flow passage 41 communicating with the inner chamber and the main valve chamber 11;
  • the spool seat 2 is provided with a spool seat through hole 23 communicating with the riser pipe 51, and the upper end port of the spool seat through hole 23 forms a spool valve port 21, and a circumferential side wall of the spool seat 2
  • the spool seat side hole 24 communicating with the spool seat through hole 23 is provided in the upper portion; when the refrigerant flows in the forward direction, the spool seat 2 closes the main valve port 441 to interrupt the sleeve flow passage 41 and the spool seat side hole 24
  • the communication between the refrigerant flows through the sleeve flow passage 41 to the spool valve port 21; when the refrigerant flows in the reverse direction, the spool seat 2 moves up to open the main valve port 441 and communicates with the spool seat side hole 24 and the slee
  • the cross tube 52 is a high pressure area, and the vertical tube
  • the side is the low pressure zone. Under the action of the refrigerant pressure difference, the spool seat 2 moves downward to close the main valve port 441. On this basis, the refrigerant enters the inner cavity of the sleeve 4 through the sleeve flow passage 41, when the valve needle When the valve spool 21 is opened, the refrigerant enters the vertical pipe 51 side through the spool valve port 21, and the valve needle member 3 can reciprocate in the axial direction with the screw rod 61, thereby adjusting the valve.
  • the opening of the core valve port 21 achieves the purpose of adjusting the flow rate of the electronic expansion valve.
  • the vertical pipe 51 is on the side of the high pressure zone, and the transverse pipe
  • the side is the low pressure zone. Under the action of the refrigerant pressure difference, the spool seat 2 moves upwards, thus opening The main valve port 441 realizes the communication between the sleeve flow path 41 and the valve body seat side hole 24, and the refrigerant flows into the main valve through the valve core seat through hole 23, the valve body seat side hole 24, the main valve port 441, and the sleeve flow path 41.
  • the cavity 11 finally enters the side of the cross-over pipe 52, thereby achieving the purpose of one-way valve one-way conduction.
  • the electronic expansion valve provided by the invention can prevent the high pressure refrigerant from causing excessive impact on the valve core seat 2, preventing eccentricity thereof, thereby avoiding the occurrence of internal leakage and ensuring the reliability of the operation of the system.
  • the main valve port 441 is different from the conventional main valve port in the prior art; in the present invention, the main valve port is The sealing portion formed by the tapered surface or the line pointed by reference numeral 441 cuts the gap between the sleeve flow path 41 and the valve body seat side hole 24 when the valve seat sealing portion 22 seals the sealing portion.
  • the lower end of the sleeve 4 is supported by the valve seat 1, and the inner wall of the lower end portion of the sleeve 4 forms a spool seat guide hole 44, and the upper orifice of the spool seat guide hole 44 is formed.
  • the main valve port 441 is formed on the inner wall of the sleeve 4, and the structure in which the main valve port 441 is opened in the valve seat 1 can facilitate the securing of the spool seat 2 and the main valve in the sleeve 4.
  • the coaxiality between the ports 441 is advantageous for improving the sealing performance.
  • valve seat 1 is provided with a vertical interface portion 13, and the lower end portion of the sleeve 4 is extended by the vertical interface portion 13 and supported by the inner wall of the vertical interface portion 13; 51 is further mounted on the circumferential outer side wall of the lower end portion of the sleeve 4.
  • This kind of structural design is realized on the one hand
  • the support of the lower end of the sleeve 4, on the other hand, also enables the installation of the riser 51.
  • the circumferential outer side wall of the valve core seat 2 is provided with a valve core outer guiding portion 25 which is guided and fitted into the valve core seat guiding hole 44, and the valve core seat is outside.
  • the tip end of the guide portion 25 protrudes outward to form a valve plug seat portion 22 that opens and closes the main valve port 441. Due to the cooperation of the outer sleeve guide portion 25 and the spool seat guide hole 44, the two can maintain a good coaxiality, thereby enabling the spool seat seal portion 22 to maintain a good coaxiality with the main valve port 441. Degree, which can improve the sealing performance between the two to prevent endoleaks.
  • the spool seat through hole 23 includes a first axial hole 231 communicating with the vertical pipe 51, and a second axial hole 232 disposed above the first axial hole 231, the second The upper end opening of the axial hole 232 forms the spool valve port 21; and the flow area of the first axial hole 231 is larger than the flow area of the second axial hole 232.
  • the spool seat side hole 24 is formed on the circumferential side wall of the valve core seat 2 where the first axial hole 231 is located, and communicates with the first axial hole 231;
  • the flow area of the spool seat side hole 24 is larger than the flow area of the first axial hole 231.
  • the valve core seat side holes 24 may be 4 to 6, and the above-mentioned "circulation area of the wide core seat side holes 24" refers to the total flow area of each of the wide core seat side holes 24. .
  • the flow area of the first axial hole 231 is larger than the flow area of the second axial hole 232, and the flow area of the wide core side hole 24 is larger than the flow area of the first axial hole 231, so that the refrigerant can be realized.
  • the flow is flown and the large flow in the reverse direction is turned on.
  • first axial hole 231 and the second axial hole 232 are further communicated through the tapered hole 233.
  • This structural design can reduce the flow resistance encountered when the refrigerant flows in the reverse direction.
  • the sleeve 4 is of a unitary structure, and the sleeve flow passage 41 is a plurality of through holes formed in the circumferential side walls of the sleeve 4.
  • the number of the through holes may be plural, for example, 4 to 6.
  • the upper part of the sleeve 4 is provided with a nut inner guiding hole 42, and the sleeve 4 is fitted with the inner guiding hole 42 of the nut to the circumferential outer wall of the lower part of the nut 62, and
  • the valve needle member 3 is disposed in the guide hole of the nut 62; on the basis of the nut inner guide hole 42, the spool guide hole and the main valve port of the sleeve 4
  • the 441 can be integrally formed, so that a good coaxiality can be maintained between the three; on the basis, the lower portion of the nut 62 is guided in the nut inner guiding hole 42, and the valve needle member 3 is provided in the guiding hole in the nut 62.
  • the spool seat 2 is disposed in the spool seat guide hole 44, so that the valve needle member 3 and the spool seat 2 can maintain a good coaxiality, so that the valve needle member 3 and the spool valve port 21 can be maintained. Better coaxiality and improved sealing performance between the two.
  • FIG. 8 is a schematic structural view of the electronic expansion valve in the forward flow of the refrigerant in the second embodiment of the present invention
  • FIG. 9 is the electronic expansion valve of FIG.
  • FIG. 10 is a structural schematic view of a valve body seat fitting portion of the sleeve of the electronic expansion valve of FIG. 8
  • FIG. 11 is a structural schematic view of a nut guide seat of the sleeve of the electronic expansion valve of FIG. 8
  • the sleeve 4 is of a split structure including a nut guide seat 43 fixed to the inner side wall of the valve seat 1, and supported by the bottom wall of the valve seat 1.
  • the spool seat fitting portion 45; the nut guide seat 43 and the spool seat fitting portion 45 form a sleeve flow passage 41 in the axial direction of the valve seat 1; the spool seat fitting portion 45 defines the spool seat 2 positioning hole And main valve port 441.
  • the sleeve 4 since the sleeve 4 has a separate structure, the gap between the nut guide seat 43 and the spool seat fitting portion 45 in the axial direction of the valve seat 1 forms the sleeve flow path 41, thereby reducing the reverse flow of the refrigerant. The pressure loss and the difficulty in processing the sleeve 4 are reduced.
  • the nut guide seat 43 is provided with a guide inner hole 431. As shown in Figs. 8 and 9, the lower portion of the nut 62 is fitted into the guide inner hole 431.
  • the side wall of the guide seat is provided with a circumferential protruding portion 432 fitted to the inner side wall of the valve seat 1, and the circumferential protruding portion 432 is provided with a plurality of communicating with the upper cavity thereof. And a gap 433 of the lower cavity.
  • the notch 433 communicates with the upper and lower cavities of the guide seat, thereby enabling refrigerant pressure balance within the electronic expansion valve system.
  • the nut guide in order to improve the coaxiality, the nut guide can be first used.
  • valve seat fitting portion 45 are welded to the valve seat 1, and then the outer circumference of the valve seat 1 is positioned to guide the inner hole 431, the valve body guide hole 44 and the main valve port 441, thereby improving the three Coaxiality.
  • the spool seat The reciprocating stroke of 2 is smaller than the reciprocating stroke of the needle member 3; on the basis of this, as shown in Figs. 5, 9, and 12, when the refrigerant flows in the reverse direction, the spool seat 2 is moved up thereto.
  • the end face 4 is biased to the lower end surface 621 of the nut 62.
  • the structural design prevents the upper end surface of the valve core seat 2 from moving up to the fourth valve needle member 3, thereby avoiding the transmission of the reverse impact to the thread of the screw rod 61, thereby avoiding reducing the life of the threaded rod 61 thread.

Landscapes

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

Abstract

一种电子膨胀阀，其主阀腔（11）内固定有套筒（4），其阀芯座（2）沿轴向可移动设于套筒（4）中；套筒（4）的周向侧壁上开设有套筒流道（41），阀芯座（2）的周向侧壁上开设有阀芯座侧孔（24）；当冷媒正向流动时，阀芯座（2）关闭主阀口（441）而中断套筒流道（41）与阀芯座侧孔（24）之间的连通，并且冷媒经由套筒流道（41）流向阀芯阀口（21）；当冷媒逆向流动时，阀芯座（2）上移开启主阀口（441）而连通阀芯座侧孔（24）与套筒流道（41）。当冷媒正向流动时，这种电子膨胀阀的结构设计能够避免高压冷媒对阀芯座（2）造成过大冲击，防止其发生偏心。

Description

一种电子膨胀阀 本申请要求于 2012 年 05 月 29 日提交中国专利局、 申请号为 201210176799.0、 发明名称为"一种电子膨胀阀"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
本发明涉及流体控制部件技术领域， 特别涉及一种电子膨胀阀。 背景技术
在空调市场， 由于其室内机与室外机距离较远， 因此采用了两个电子 膨胀阀， 而两个电子膨胀阀必须分别并联单向阀才能最大限度的提高系统 效率。 其系统原理图如图 1 , 工作原理筒述如下：
制冷时： 从压缩机 7'8排气管出来的高温高压的气态制冷剂通过四通 阀 7Ί的 D接管、 E接管、 室外交换器 7'2 (冷凝放热）、第一单向阀 7'4 (第 一电子膨胀阀 7'3不起调节作用）、 第二电子膨胀阀 7'5 (此时第二单向阀 7'6关闭， 第二电子膨胀阀 7'5起流量调节作用）， 最终进入室内交换器 77 蒸发吸收热量制冷。 此时由于第二电子膨胀阀 7'6与室内交换器 77较近， 可以减少热量损失（如果电子膨胀阀距离蒸发器太远， 那么从电子膨胀阀 出来的低温低压的液态制冷剂很容易气化， 不仅造成热损失， 也使得蒸发 器利用率大幅度下降）。 同时， 从室外换热器 7'2出来的中温、 高压的制冷 剂如果从第一电子膨胀阀 7'3 经过， 即使在膨胀阀全开的条件下， 仍会出 现节流效果， 降低了制冷剂的压力， 待传到第二电子膨胀阀 7'5 时制冷剂 很可能会部分气化， 影响电子膨胀阀的节流效果， 降低系统效率。
制热时： 从压缩机 7'8排气管出来的高温高压的气态制冷剂通过四通 阀 7Ί的 D接管、 C接管、 室内交换器 77 (冷凝放热）、第二单向阀 7'6 (第 二电子膨胀阀 7'5不起调节作用）、 第一电子膨胀阀 7'3 (此时第一单向阀 7'4关闭， 第一电子膨胀阀 7'3起流量调节作用）， 最终进入室外交换器 7'2 蒸发吸收热量制冷。 此时由于第一电子膨胀阀 7'3与室外交换器 7'2较近， 可以减少热量损失（如果电子膨胀阀距离蒸发器太远， 那么从电子膨胀阀 出来的低温低压的液态制冷剂很容易气化， 不仅造成热损失， 也使得蒸发 器利用率大幅度下降）。 同时， 从室内换热器 77出来的中温、 高压的制冷 剂如果从第二电子膨胀阀 7'5 经过， 即使在膨胀阀全开的条件下， 仍会出 现节流效果， 降低了制冷剂的压力， 待流到第一电子膨胀阀 7'3 时制冷剂 会部分气化， 影响电子膨胀阀的节流效果， 降低系统效率。
但是， 目前市场上有客户要求将单向阀和电子膨胀阀合并， 从而减少 零部件， 减少焊点， 进而提高系统的可靠性。
鉴于此， 现有技术中， 专利号为 "特开 2009-287913" 的日本专利公 开了一种带单向阀功能的电子膨胀阀， 具体地， 请参考图 2和图 3 , 图 2 为现有技术中的电子膨胀阀正向进行流量调节时的结构示意图， 图 3为现 有技术中的电子膨胀阀逆向导通时的结构示意图。
如图 2和图 3所示， 该现有技术中的电子膨胀阀包括阀座 1', 阀座 1' 设有主阀腔 1'1、 横接口部 Γ2和竖接口部 Γ3 , 该竖接口部 Γ3的上端开口 形成主阀口 Γ31 ; 主阀腔 1Ί内设有阀芯座 2',该阀芯座 2'以其周向侧壁与 主阀腔 1Ί的周向内侧壁贴合导向， 以便可沿主阀腔 1Ί的轴向往复运动， 从而开启和关闭主阀口 1'31； 此外， 如图 2和图 3所示， 该阀芯座 2'设有 副阀腔 2Ί , 阀芯座 2'设有与该副阀腔 2Ί连通的阀芯阀口 2'2, 阀针部件
3'伸入该副阀腔 2Ί中并沿轴向往复运动，从而开启和关闭该阀芯阀口 2'2； 再者， 如图 2和图 3所示， 阀芯座 2'的周向侧壁上还开设有与副阀腔 2Ί 连通的导通孔 2'3 , 该导通孔 2'3朝向横接口部 Γ2, 并连通副阀腔 2Ί与横 接口部 1'2。
此外， 如图 2和图 3所示， 横接口部 1 '2连接有横接管 4Ί , 竖接口部 1'3连接有竖接管 4'2, 冷媒流体由横接管 4Ί向竖接管 4'2流动时（亦即横 接口部 1 '2—侧为高压区， 竖接口部 Γ3—侧为低压区 ) 定位为正向流动， 冷媒流体由竖接管 1'3向横接管 1'2流动时 （亦即竖接口部 1'3—侧为高压 区， 横接口部 1 '2—侧为低压区 )定位为逆向流动。 阀针部件 3'与丝杆 5Ί 连接， 丝杆 5Ί与螺母 5'2通过螺纹配合； 在该种结构中， 在线圈 6Ί磁场 的作用下， 磁体 6'2转动， 丝杆 5Ί转动并由于螺母 5'2螺纹配合因而沿轴 向往复运动， 从而带动阀针部件 3'沿轴向往复运动， 以便开启或关闭阀芯 阀口 2'2。
如图 2所示， 冷媒正向流动时， 横接口部 Γ2—侧为高压区， 竖接口 部 1'3 —侧为低压区， 在冷媒压力差的作用下， 阀芯座 2'向下运动， 从而 关闭主阀口 1'31； 在此基础上， 冷媒由横接口部 1'2通过导通孔 2'3进入副 阀腔 2Ί , 阀针部件 3'开启阀芯阀口 2'2, 进入副阀腔 2Ί中的冷媒由该阀芯 阀口 2'2流向竖接口部 1'3 , 进而流向竖接管 4'2中。 在该工作过程中， 通 过丝杆 5Ί沿轴向运动， 可以使得阀针部件 3'调节阀芯阀口 2'2的开度， 进 而实现电子膨胀阀流量调节的目的。
如图 3所示， 冷媒逆向流动时， 竖接口部 Γ3—侧为高压区， 横接口 部 1'2—侧为低压区， 此时， 在冷媒压力差的作用下， 推动阀芯座 2'向上 运动， 从而开启主阀口 Γ31 , 冷媒经过主阀口 1'31、 主阀腔 1Ί和横接口部 1'2, 流向横接管 4Ί , 从而实现单向阀的单向导通功能。
然而， 上述现有技术中的电子膨胀阀存在如下缺陷：
如图 2所示， 当冷媒正向流动时， 由于阀芯座 2'的侧壁正对横接口部
1'2, 因而阀芯座 2'的周向侧壁会受到高压冷媒的冲击； 当冷媒压力出现波 动时， 会造成该阀芯座 2'偏心， 从而造成阀芯座 2'对主阀口 Γ31的密封不 严， 造成内漏偏大， 影响系统的工作性能。 此外， 阀芯座 2'偏心也会造成 阀针部件 3'与阀芯阀口 2'2出现干涉。 发明内容
本发明要解决的技术问题为提供一种电子膨胀阀， 当冷媒正向流动 时， 该电子膨胀阀的结构设计能够避免高压冷媒对阀芯座造成过大冲击， 防止其发生偏心， 从而避免内漏的发生， 保证系统的工作的可靠性。
为解决上述技术问题， 本发明提供一种电子膨胀阀， 包括阀座、 竖接 管和横接管， 所述阀座设有主阀腔； 所述电子膨胀阀还包括与所述竖接管 连通的主阀口及可开启和关闭该主阀口的阀芯座， 所述阀芯座设有可与所 述竖接管连通的阀芯阀口， 所述电子膨胀阀还包括可开启和关闭该阀芯阀 口的阀针部件；所述电子膨胀阀还包括驱动阀针部件轴向运动的驱动部件， 该驱动部件包括丝杆及与该丝杆螺纹配合的螺母；
当冷媒正向流动时， 所述阀芯座关闭主阀口， 冷媒经由所述阀芯阀口 流向竖接管，所述阀针部件在驱动部件的驱动下调节所述阀芯阀口的开度； 当冷媒逆向移动时， 所述阀芯座上移开启主阀口， 冷媒经由所述主阀口流 向横接管；
所述主阀腔内固定有套筒，所述阀芯座沿轴向可移动设于所述套筒中， 所述阀针部件的下部伸入所述套筒中开启和关闭所述阀芯阀口；
所述套筒的周向侧壁上开设有连通其内腔与所述主阀腔的套筒流道； 所述阔芯座设有与所述竖接管连通的阔芯座通孔， 并该阔芯座通孔的上端 孔口形成所述阀芯阀口， 所述阀芯座的周向侧壁上开设有与该阀芯座通孔 连通的阀芯座侧孑 L;
当冷媒正向流动时， 所述阀芯座关闭主阀口而中断套筒流道与阀芯座 侧孔之间的连通， 并冷媒经由该套筒流道流向所述阀芯阀口； 当冷媒逆向 流动时， 所述阀芯座上移开启主阀口而连通所述阀芯座侧孔与套筒流道。
优选地， 所述套筒的下端由阀座支撑， 并所述套筒下端部的内壁形成 阀芯座导向孔， 所述阀芯座导向孔的上部孔口形成所述主阀口。
优选地， 所述阀座上开设有竖接口部， 所述套筒的下端部由所述竖接 口部伸出， 并由该竖接口部的内壁支撑；
优选地，所述竖接管进一步安装于所述套筒的下端部的周向外侧壁上。 优选地， 所述阀芯座的周向外侧壁设有导向配合于所述阀芯座导向孔 中的阀芯座外导向部， 该阀芯座外导向部的顶端向外凸出形成开启和关闭 所述主阀口的阀芯座密封部。
优选地， 所述阔芯座通孔包括与所述竖接管连通的第一轴向孔、 及设 于该第一轴向孔上方的第二轴向孔， 该第二轴向孔的上端孔口形成所述阀 芯阔口； 并，所述第一轴向孔的流通面积大于所述第二轴向孔的流通面积。
优选地， 所述阀芯座侧孔开设于所述第一轴向孔所在的阀芯座周向侧 壁上， 并与该第一轴向孔连通； 并， 所述阔芯座侧孔总的流通面积大于所 述第一轴向孔的流通面积。
优选地， 所述第一轴向孔与第二轴向孔进一步通过锥形孔连通。 优选地， 所述套筒为一体结构， 所述套筒流道为多个开设于套筒周向 侧壁上的通孔。
优选地， 所述套筒的上部设有螺母内导向孔， 所述套筒以该螺母内导 向孔配合于所述螺母的下部的周向外壁上。
优选地， 所述套筒为分体结构， 包括固定于所述阀座的内侧壁上螺母 导向座、 及由阀座的底壁支撑的阀芯座配合部； 该螺母导向座与所述阀芯 座配合部在阀座轴向上的间隙形成所述套筒流道。
优选地， 所述螺母导向座设有导向内孔， 所述螺母的下部导向配合于 该导向内孔中。
优选地， 所述导向座的侧壁设有配合于所述阀座的内侧壁上的周向凸 出部， 并该周向凸出部设有多个连通该其上方腔体和下方腔体的缺口。
优选地， 所述阀芯座的往复运动行程小于所述阀针部件的往复运动行 程， 以便该阀芯座上移而以其上端面抵接螺母的下端面而限位。
在现有技术的基础上， 本发明所提供的电子膨胀阀的主阀腔内固定有 套筒， 所述阀芯座沿轴向可移动设于所述套筒中， 所述阀针部件的下部伸 入所述套筒中开启和关闭所述阀芯阀口； 所述套筒的周向侧壁上开设有连 通其内腔与所述主阀腔的套筒流道； 所述阀芯座设有与所述竖接管连通的 阀芯座通孔， 并该阀芯座通孔的上端孔口形成所述阀芯阀口， 所述阀芯座 的周向侧壁上开设有与该阀芯座通孔连通的阀芯座侧孔； 当冷媒正向流动 时， 所述阀芯座关闭主阀口而中断套筒流道与阀芯座侧孔之间的连通， 并 冷媒经由该套筒流道流向所述阀芯阀口； 当冷媒逆向流动时， 所述阀芯座 上移开启主阀口而连通所述阀芯座侧孔与套筒流道。
当冷媒正向流动时， 横接管一侧为高压区， 竖接管一侧为低压区， 在 冷媒压力差的作用下， 阀芯座向下运动关闭主阀口； 在此基础上， 冷媒通 过套筒流道进入套筒内腔， 当阀针部件开启阀芯阀口时， 冷媒又通过该阀 芯阀口进入竖接管一侧， 在此过程中， 阀针部件可以随着丝杆沿轴向往复 运动， 从而调节阀芯阀口的开度， 实现电子膨胀阀流量调节的目的。
当冷媒逆向流动时， 竖接管一侧为高压区， 横接管一侧为低压区， 在 冷媒压力差的作用下， 阀芯座向上移动， 从而开启主阀口而实现套筒流道 与阀芯座侧孔的连通， 冷媒通过阀芯座通孔、 阀芯座侧孔、 主阀口和套筒 流道流入主阀腔，最终进入横接管一侧，从而实现单向阀单向导通的目的。
在上述工作过程中， 当冷媒正向流动时， 由于阀芯座设于套筒中， 并 且套筒固定设于主阀腔中， 因而高压冷媒对阀芯座的压力冲击大部分由套 筒承受， 因而阀芯座受到的冲击能够明显减小， 因而可以防止其发生偏心， 从而避免内漏的发生， 保证系统的工作的可靠性。
综上所述， 本发明提供的电子膨胀阀能够避免高压冷媒对阀芯座造成 过大冲击， 防止其发生偏心， 从而避免内漏的发生， 保证系统的工作的可 靠性。 附图说明
图 1为现有技术中空调制冷系统的工作原理示意图；
图 2为现有技术中的电子膨胀阀正向进行流量调节时的结构示意图； 图 3为现有技术中的电子膨胀阀逆向导通时的结构示意图；
图 4为本发明第一种实施例中电子膨胀阀在冷媒正向流动时的结构示 意图；
图 5为图 4中的电子膨胀阀在冷媒逆向流动时的结构示意图； 图 6为图 4中电子膨胀阀的套筒的结构示意图；
图 7为图 4中电子膨胀阀的阀芯座的结构示意图；
图 8为本发明第二种实施例中电子膨胀阀在冷媒正向流动时的结构示 意图；
图 9为图 8中的电子膨胀阀在冷媒逆向流动时的结构示意图； 图 10为图 8中电子膨胀阀的套筒的阀芯座配合部的结构示意图； 图 11为图 8中电子膨胀阀的套筒的螺母导向座的结构示意图； 图 12和图 4和图 8中电子膨胀阀的螺母的结构示意图。 其中， 图 1至图 3中附图标记与部件名称之间的对应关系为：
Γ阀座； 1Ί主阀腔； Γ2横接口部； Γ3竖接口部； Γ31主阀口； 2'阀芯座； 2Ί副阀腔； 2'2阀芯阀口； 2'3导通孔； 3'阀针部件；
4Ί横接管； 4'2竖接管；
5Ί丝杆； 5'2螺母；
6Ί线圈； 6'2磁体；
7Ί四通阀； T2室外换热器； 7'3第一电子膨胀阀； 7'4第一单向阀；
Figure imgf000008_0001
二电子膨胀阀； 7'6第二单向阀； 77室内换热器； 7'8压缩机。 图 4至图 12中附图标记与部件名称之间的对应关系为：
1阀座； 11主阀腔； 12横接口部； 13竖接口部；
2阀芯座； 21阀芯阀口； 22阀芯座密封部； 23阀芯座通孔； 231第一 轴向孔； 232第二轴向孔； 233锥形孔； 24阀芯座侧孔； 25阀芯座外导向 部；
3阀针部件；
4套筒； 41套筒流道； 42螺母内导向孔； 43螺母导向座； 431导向内 孔； 432周向凸出部； 433缺口； 44阀芯座导向孔； 441主阀口； 45阀芯 座配合部； 51竖接管； 52横接管；
61丝杆； 62螺母； 621螺母的下端面。 具体实施方式
本发明的核心为提供一种电子膨胀阀， 当冷媒正向流动时， 该电子膨 胀阀的结构设计能够避免高压冷媒对阀芯座造成过大冲击， 防止其发生偏 心， 从而避免内漏的发生， 保证系统的工作的可靠性。
为了使本领域的技术人员更好地理解本发明的技术方案， 下面结合附 图和具体实施例对本发明作进一步的详细说明。
请参考图 4、 图 5、 图 6和图 7 , 图 4为本发明第一种实施例中电子膨 胀阀在冷媒正向流动时的结构示意图； 图 5为图 4中的电子膨胀阀在冷媒 逆向流动时的结构示意图；图 6为图 4中电子膨胀阀的套筒的结构示意图； 图 7为图 4中电子膨胀阀的阀芯座的结构示意图。
在基础技术方案中，如图 4和图 5所示，本发明所提供的电子膨胀阀， 包括阀座 1 , 阀座 1设有主阀腔 11、 横接口部 12和竖接口部 13 , 横接口 部 12安装有横接管 52, 竖接口部 13安装有竖接管 51 ; 电子膨胀阀还包括 与竖接管 51连通的主阀口 441及可开启和关闭该主阀口 441的阀芯座 2, 阀芯座 2设有可与竖接管 51连通的阀芯阀口 21 , 电子膨胀阀还包括可开 启和关闭该阀芯阀口 21的阀针部件 3; 电子膨胀阀还包括驱动阀针部件 3 轴向运动的驱动部件， 该驱动部件包括丝杆 61及与该丝杆 61螺纹配合的 螺母 62。
如图 4和图 5所示， 当冷媒正向流动时， 阀芯座 2关闭主阀口 441 , 冷媒经由阀芯阀口 21流向竖接管 51 , 阀针部件 3在驱动部件的驱动下调 节阀芯阀口 21的开度； 当冷媒逆向移动时，阀芯座 2上移开启主阀口 441 , 冷媒经由主阀口 441流向横接管 52。
在上述结构的基础上，如图 4和图 5所示，主阀腔 11内固定有套筒 4, 阀芯座 2沿轴向可移动设于套筒 4中， 阀针部件 3的下部伸入套筒 4中开 启和关闭阀芯阀口 21 ; 如图 6所示， 套筒 4的周向侧壁上开设有连通其内 腔与主阀腔 11的套筒流道 41； 如图 7所示， 阀芯座 2设有与竖接管 51连 通的阀芯座通孔 23 , 并该阀芯座通孔 23的上端孔口形成阀芯阀口 21 , 阀 芯座 2的周向侧壁上开设有与该阀芯座通孔 23连通的阀芯座侧孔 24； 当 冷媒正向流动时，阀芯座 2关闭主阀口 441而中断套筒流道 41与阀芯座侧 孔 24之间的连通， 并冷媒经由该套筒流道 41流向阀芯阀口 21 ; 当冷媒逆 向流动时，阀芯座 2上移开启主阀口 441而连通阀芯座侧孔 24与套筒流道 41。
当冷媒正向流动时， 如图 4所示， 横接管 52—侧为高压区， 竖接管
51 —侧为低压区， 在冷媒压力差的作用下， 阀芯座 2向下运动关闭主阀口 441 ; 在此基础上， 冷媒通过套筒流道 41进入套筒 4内腔， 当阀针部件 3 开启阀芯阀口 21时，冷媒又通过该阀芯阀口 21进入竖接管 51—侧，在此 过程中， 阀针部件 3可以随着丝杆 61沿轴向往复运动，从而调节阀芯阀口 21的开度， 实现电子膨胀阀流量调节的目的。
当冷媒逆向流动时， 如图 5所示， 竖接管 51—侧为高压区， 横接管
52—侧为低压区， 在冷媒压力差的作用下， 阀芯座 2向上移动， 从而开启 主阀口 441而实现套筒流道 41与阀芯座侧孔 24的连通， 冷媒通过阀芯座 通孔 23、 阀芯座侧孔 24、 主阀口 441和套筒流道 41流入主阀腔 11 , 最终 进入横接管 52—侧， 从而实现单向阀单向导通的目的。
在上述工作过程中， 当冷媒正向流动时， 由于阀芯座 2设于套筒 4中 , 并且套筒 4固定设于主阀腔 11中，因而高压冷媒对阀芯座 2的压力冲击大 部分由套筒 4承受， 因而阀芯座 2受到的冲击能够明显减小， 因而可以防 止其发生偏心， 从而避免内漏的发生， 保证系统的工作的可靠性。
综上， 本发明提供的电子膨胀阀能够避免高压冷媒对阀芯座 2造成过 大冲击， 防止其发生偏心， 从而避免内漏的发生， 保证系统的工作的可靠 性。
需要说明的是， 在本发明中， 结合图 4、 图 5、 图 6和图 7所示， 主 阀口 441不同于前文现有技术中传统的主阀口； 在本发明中， 主阀口实为 附图标记 441所指向的锥形面或线所形成的密封部位， 当阀芯座密封部 22 密封该密封部位时， 便会切断套筒流道 41与阀芯座侧孔 24之间的连通； 当阀芯座上移一' 离而阀芯座侧孔 24并没有露出时，此时由于阀芯座 密封部 22与主阀口 441之间的密封部位已经开启，因而冷媒经过阀芯座侧 孔 24、 阀芯座外导向部 25与阀芯座导向孔 44的内壁之间的间隙和主阀口 441进入套筒流道 41 ;当阀芯座上移足够距离而使得阀芯座侧孔 24部分露 出或完全露出时， 冷媒可以经由阀芯座侧孔 24直接流向套筒流道 41 , 而 不再经过主阀口 441 , 因而不用于现有技术中冷媒始终要经过主阀口。
在上述基础技术方案中， 可以作出进一步改进。 具体地， 如图 4和图 5所示， 套筒 4的下端由阀座 1支撑， 并套筒 4下端部的内壁形成阀芯座 导向孔 44, 阀芯座导向孔 44的上部孔口形成主阀口 441。 在该种结构中， 在套筒 4的内壁上加工形成主阀口 441 , 相对于在阀座 1开设主阀口 441 的结构，能够有利于保证套筒 4中的阀芯座 2与主阀口 441之间的同轴度， 从而有利于提高密封性能。
进一步地， 如图 4和图 5所示， 阀座 1上开设有竖接口部 13 , 套筒 4 的下端部由竖接口部 13伸出， 并由该竖接口部 13的内壁支撑； 竖接管 51 进一步安装于套筒 4的下端部的周向外侧壁上。 该种结构设计一方面实现 了对套筒 4下端部的支撑， 另一方面也实现了竖接管 51的安装。
进一步地， 请同时参考图 4、 图 5和图 7 , 阀芯座 2的周向外侧壁设有 导向配合于阀芯座导向孔 44中的阀芯座外导向部 25 , 该阀芯座外导向部 25的顶端向外凸出形成开启和关闭主阀口 441的阀芯座密封部 22。由于阀 芯座外导向部 25与阀芯座导向孔 44的配合， 使得二者能够保持较好的同 轴度，进而能够使得阀芯座密封部 22与主阀口 441保持较好的同轴度，从 而能够提高二者之间的密封性能， 防止发生内漏。
在上述技术方案的基础上，还可以对阀芯座 2作出进一步改进。 比如， 如图 7所示， 阀芯座通孔 23包括与竖接管 51连通的第一轴向孔 231、 及 设于该第一轴向孔 231上方的第二轴向孔 232, 该第二轴向孔 232的上端 孔口形成阀芯阀口 21 ;并，第一轴向孔 231的流通面积大于第二轴向孔 232 的流通面积。 在此基础上， 如图 7所示， 阀芯座侧孔 24开设于第一轴向孔 231所在的阀芯座 2周向侧壁上， 并与该第一轴向孔 231连通； 并， 阀芯 座侧孔 24的流通面积大于第一轴向孔 231的流通面积。需要说明的是， 阀 芯座侧孔 24可以为 4至 6个， 在此基础上， 上述 "阔芯座侧孔 24的流通 面积" 指得是各个阔芯座侧孔 24的总的流通面积。
在上述结构中， 第一轴向孔 231的流通面积大于第二轴向孔 232的流 通面积，并阔芯座侧孔 24的流通面积大于第一轴向孔 231的流通面积， 因 而能够实现冷媒正向时节流流动和逆向时的大流量导通。
此外， 如图 7所示， 第一轴向孔 231与第二轴向孔 232进一步通过锥 形孔 233连通。 该种结构设计能够减少冷媒逆向流动时受到的流阻。
在上述基础技术方案中， 可以作出进一步改进， 从而得到本发明的第 一种实施例。 具体地， 如图 4、 图 5和图 6所示， 套筒 4为一体结构， 套 筒流道 41为多个开设于套筒 4周向侧壁上的通孔。该通孔的数量可以为多 个， 比如 4至 6个。
在该第一种实施例中， 还可以作出进一步设计。 比如， 请参考图 4、 图 5和图 6, 套筒 4的上部设有螺母内导向孔 42, 套筒 4以该螺母内导向 孔 42配合于螺母 62的下部的周向外壁上， 并且， 阀针部件 3设于螺母 62 的导向孔中； 在基础上， 套筒 4的螺母内导向孔 42、 阀芯导向孔和主阀口 441可以一体加工形成， 因而三者之间能够保持较好的同轴度； 在基础上， 螺母 62的下部导向设于螺母内导向孔 42中，阀针部件 3设于螺母 62中的 导向孔中， 阀芯座 2设于阀芯座导向孔 44中， 因而阀针部件 3与阀芯座 2 能够保持较好的同轴度，使得阀针部件 3与阀芯阀口 21之间能够保持较好 的同轴度， 提高二者之间的密封性能。
在上述基础技术方案中， 还可以作出进一步改进， 从而得到本发明的 第二种实施例。 具体地， 请参考图 8至图 12, 图 8为本发明第二种实施例 中电子膨胀阀在冷媒正向流动时的结构示意图； 图 9为图 8中的电子膨胀 阀在冷媒逆向流动时的结构示意图；图 10为图 8中电子膨胀阀的套筒的阀 芯座配合部的结构示意图；图 11为图 8中电子膨胀阀的套筒的螺母导向座 的结构示意图； 图 12和图 4和图 8中电子膨胀阀的螺母的结构示意图。
在该第二种实施例中， 如图 8和图 9所示， 套筒 4为分体结构， 包括 固定于阀座 1的内侧壁上螺母导向座 43、及由阀座 1的底壁支撑的阀芯座 配合部 45; 该螺母导向座 43与阀芯座配合部 45在阀座 1轴向上的间隙形 成套筒流道 41 ; 阀芯座配合部 45上开设阀芯座 2定位孔和主阀口 441。
在该种结构设计中， 由于套筒 4为分体结构， 螺母导向座 43与阀芯 座配合部 45在阀座 1轴向上的间隙形成套筒流道 41 , 因而能够减少冷媒 逆向流动时的压力损失， 并且降低了套筒 4的加工难度。
此外， 如图 11所示， 螺母导向座 43设有导向内孔 431 , 如图 8和图 9 所示， 螺母 62的下部导向配合于该导向内孔 431中。 并且， 如图 11所示， 导向座的侧壁设有配合于阀座 1的内侧壁上的周向凸出部 432, 并该周向 凸出部 432设有多个连通该其上方腔体和下方腔体的缺口 433。该缺口 433 连通了导向座的上方腔体和下方腔体， 因而能够使得电子膨胀阀系统内部 实现冷媒压力平衡。
在上述套筒 4的分体结构中， 为了提高同轴度， 可以先将螺母导向座
43和阀芯座配合部 45焊接于阀座 1上， 然后再以阀座 1的外圆定位一体 车加工导向内孔 431、 阀芯座导向孔 44和主阀口 441 , 从而能够提高三者 的同轴度。
此外， 在上述两种实施例中， 还可以作出进一步改进。 比如， 阀芯座 2的往复运动行程小于阀针部件 3的往复运动行程； 在此基础上， 如图 5、 图 9和图 12所示， 当冷媒逆向流动时， 以便该阀芯座 2上移而以其上端面 4氐接螺母 62的下端面 621而限位。该种结构设计可以防止阀芯座 2上端面 上移 4氏接阀针部件 3 , 进而避免将逆向冲击传递给丝杆 61的螺纹， 避免降 低丝杆 61螺紋的寿命。
以上对本发明所提供的一种电子膨胀阀进行了详细介绍。 本文中应用 是用于帮助理解本发明的方法及其核心思想。 应当指出， 对于本技术领域 的普通技术人员来说， 在不脱离本发明原理的前提下， 还可以对本发明进 行若干改进和修饰，这些改进和修饰也落入本发明权利要求的保护范围内。

Claims

权 利 要 求
1、 一种电子膨胀阀， 包括阀座（1)、 竖接管 （51)和横接管 （52), 所述阀座（ 1 )设有主阀腔（ 11 );所述电子膨胀阀还包括与所述竖接管（ 51 ) 连通的主阀口 （441)及可开启和关闭该主阀口 （441 ) 的阀芯座（2), 所 述阀芯座（2)设有可与所述竖接管 （51 )连通的阀芯阀口 （21 ), 所述电 子膨胀阀还包括可开启和关闭该阀芯阀口 （21 ) 的阀针部件（3); 所述电 子膨胀阀还包括驱动阀针部件（3)轴向运动的驱动部件， 该驱动部件包括 丝杆（61 )及与该丝杆（61) 螺纹配合的螺母（62);
当冷媒正向流动时， 所述阀芯座（2)关闭主阀口 （441), 冷媒经由所 述阀芯阀口 （21 ) 流向竖接管 （51), 所述阀针部件 （3)在驱动部件的驱 动下调节所述阀芯阀口（21)的开度； 当冷媒逆向移动时， 所述阀芯座（2) 上移开启主阀口 （441), 冷媒经由所述主阀口 （441) 流向横接管 （52); 其特征在于， 所述主阀腔（11) 内固定有套筒 （4), 所述阀芯座（2) 沿轴向可移动设于所述套筒 （4) 中， 所述阀针部件 （3) 的下部伸入所述 套筒 （4) 中开启和关闭所述阀芯阀口 （21);
所述套筒（4)的周向侧壁上开设有连通其内腔与所述主阀腔（11)的 套筒流道（ 41 );所述阀芯座（ 2 )设有与所述竖接管连通的阀芯座通孔（ 23 ), 并该阀芯座通孔（23 )的上端孔口形成所述阀芯阀口（21),所述阀芯座（2) 的周向侧壁上开设有与该阀芯座通孔（ 23 )连通的阀芯座侧孔（ 24 );
当冷媒正向流动时， 所述阀芯座（2) 关闭主阀口 （441) 而中断套筒 流道（ 41 )与阀芯座侧孔（ 24 )之间的连通， 并冷媒经由该套筒流道 (41 ) 流向所述阀芯阀口 （ 21 ); 当冷媒逆向流动时， 所述阀芯座（ 2 )上移开启 主阀口 （441) 而连通所述阀芯座侧孔（24)与套筒流道（41)。
2、 如权利要求 1所述的电子膨胀阀， 其特征在于， 所述套筒 （4) 的 下端由阀座（1) 支撑， 并所述套筒 （4) 下端部的内壁形成阀芯座导向孔
(44), 所述阀芯座导向孔（44) 的上部孔口形成所述主阀口 （441)。
3、 如权利要求 2所述的电子膨胀阀， 其特征在于， 所述阀座（1)上 开设有竖接口部 （13), 所述套筒 （4) 的下端部由所述竖接口部 （13)伸 出， 并由该竖接口部 （13) 的内壁支撑。 4、 如权利要求 3所述的电子膨胀阀， 其特征在于， 所述竖接管 （51) 进一步安装于所述套筒 （4) 的下端部的周向外侧壁上。
5、 如权利要求 2至 4任一项所述的电子膨胀阀， 其特征在于， 所述阀 芯座（2)的周向外侧壁设有导向配合于所述阀芯座导向孔（44)中的阀芯 座外导向部（25), 该阀芯座外导向部（25)的顶端向外凸出形成开启和关 闭所述主阀口 （ 441 ) 的阀芯座密封部 （ 22 )。
6、 如权利要求 1至 4任一项所述的电子膨胀阀， 其特征在于， 所述阀 芯座通孔（23) 包括与所述竖接管 （51 )连通的第一轴向孔（231)、 及设 于该第一轴向孔（231 )上方的第二轴向孔（232), 该第二轴向孔（232) 的上端孔口形成所述阔芯阔口 （21); 并， 所述第一轴向孔（231 ) 的流通 面积大于所述第二轴向孔（ 232 ) 的流通面积。
7、如权利要求 6所述的电子膨胀阀，其特征在于，所述阀芯座侧孔（ 24 ) 开设于所述第一轴向孔（231)所在的阀芯座（2)周向侧壁上， 并与该第 一轴向孔（231)连通； 并， 所述阔芯座侧孔（24)总的流通面积大于所述 第一轴向孔（231 ) 的流通面积。
8、 如权利要求 6 所述的电子膨胀阀， 其特征在于， 所述第一轴向孔 (231)与第二轴向孔（232)进一步通过锥形孔（233 )连通。
9、 如权利要求 1至 8任一项所述的电子膨胀阀， 其特征在于， 所述套 筒 （4)为一体结构， 所述套筒流道（41 )为多个开设于套筒 （4)周向侧 壁上的通孔。
10、 如权利要求 9所述的电子膨胀阀， 其特征在于， 所述套筒（4)的 上部设有螺母内导向孔（42), 所述套筒 （4) 以该螺母内导向孔（42) 配 合于所述螺母（62) 的下部的周向外壁上。
11、 如权利要求 1至 8任一项所述的电子膨胀阀， 其特征在于， 所述 套筒 （4) 为分体结构， 包括固定于所述阀座（1) 的内侧壁上螺母导向座
( 43 )、及由阀座（ 1 )的底壁支撑的阀芯座配合部（ 45 );该螺母导向座（ 43 ) 与所述阀芯座配合部 （45)在阀座轴向上的间隙形成所述套筒流道（41)。
12、 如权利要求 11所述的电子膨胀阀， 其特征在于， 所述螺母导向座 (43)设有导向内孔（431), 所述螺母（62) 的下部导向配合于该导向内 孔（431) 中。
13、 如权利要求 11所述的电子膨胀阀， 其特征在于， 所述螺母导向座 (43) 的侧壁设有配合于所述阀座（1 ) 的内侧壁上的周向凸出部 （432), 并该周向凸出部 （432 )设有多个连通该其上方腔体和下方腔体的缺口 ( 433 )。
14、 如权利要求 1至 8任一项所述的电子膨胀阀， 其特征在于， 所述 阀芯座（2) 的往复运动行程小于所述阀针部件 （3) 的往复运动行程， 以 便该阀芯座（2)上移而以其上端面 4氏接螺母（62) 的下端面 （621 ) 而限 位。
PCT/CN2012/079932 2012-05-29 2012-08-10 一种电子膨胀阀 WO2013177865A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US14/401,484 US9341399B2 (en) 2012-05-29 2012-08-10 Electronic expansion valve

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201210176799.0 2012-05-29
CN201210176799.0A CN103453699B (zh) 2012-05-29 2012-05-29 一种电子膨胀阀

Publications (1)

Publication Number Publication Date
WO2013177865A1 true WO2013177865A1 (zh) 2013-12-05

Family

ID=49672336

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2012/079932 WO2013177865A1 (zh) 2012-05-29 2012-08-10 一种电子膨胀阀

Country Status (3)

Country Link
US (1) US9341399B2 (zh)
CN (1) CN103453699B (zh)
WO (1) WO2013177865A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111734883A (zh) * 2019-03-25 2020-10-02 株式会社鹭宫制作所 温度式膨胀阀及具备该温度式膨胀阀的冷冻循环系统

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103512288B (zh) * 2012-06-20 2016-07-06 浙江三花股份有限公司 一种电子膨胀阀
CN104776655B (zh) * 2014-01-11 2018-05-08 苏州恒兆空调节能科技有限公司 一种改进型变频空调器
CN105241131B (zh) * 2014-06-17 2019-06-04 浙江盾安人工环境股份有限公司 电子膨胀阀
CN104089024B (zh) * 2014-06-27 2016-08-24 珠海格力电器股份有限公司 限位结构及压降装置
CN105716335B (zh) * 2014-12-03 2019-09-17 浙江盾安人工环境股份有限公司 一种电子膨胀阀
CN106439150A (zh) * 2015-08-10 2017-02-22 浙江三花智能控制股份有限公司 阀的壳体组件及阀
CN106545660B (zh) * 2015-09-23 2020-04-10 盾安环境技术有限公司 一种电子膨胀阀
CN107356024B (zh) * 2016-05-10 2021-07-13 浙江盾安人工环境股份有限公司 电子膨胀阀
CN107588204A (zh) * 2016-07-08 2018-01-16 艾默生过程管理(天津)阀门有限公司 级联可控流体控制阀以及用于流体控制阀的阀内件
CN106439211B (zh) * 2016-10-12 2024-04-26 诸暨市亿霸电子阀门有限公司 一种电子膨胀阀上的阀杆组件
DE102016013492A1 (de) * 2016-11-11 2018-05-17 Hanon Systems Expansions- und Absperrventil
CN106678421B (zh) * 2017-01-12 2024-02-02 诸暨市亿霸电子阀门有限公司 一种流量控制精度的电子膨胀阀
JP6903453B2 (ja) * 2017-03-10 2021-07-14 株式会社鷺宮製作所 電動弁および冷凍サイクルシステム
EP3617615A4 (en) * 2017-04-28 2021-01-20 Zhejiang Sanhua Intelligent Controls Co., Ltd. REFRIGERATOR VALVE DEVICE AND REFRIGERATION SYSTEM INCLUDING THIS VALVE DEVICE
CN107906214B (zh) * 2017-12-14 2023-05-19 浙江中宝自控元件有限公司 一种流量控制阀
CN111140687A (zh) * 2018-11-06 2020-05-12 浙江三花智能控制股份有限公司 电子膨胀阀
CN112146312A (zh) * 2019-06-28 2020-12-29 浙江三花智能控制股份有限公司 电子膨胀阀
CN112963614A (zh) * 2019-11-27 2021-06-15 浙江盾安禾田金属有限公司 降噪套以及电子膨胀阀
CN113623404A (zh) * 2021-08-10 2021-11-09 翟维友 一种电子膨胀阀及制冷设备

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100552942B1 (ko) * 2002-12-02 2006-02-22 가부시기가이샤 후지고오키 전동 밸브
CN200968423Y (zh) * 2006-11-16 2007-10-31 鞍山电磁阀有限责任公司 智能型套筒式高温高压电磁阀
JP4285155B2 (ja) * 2003-08-27 2009-06-24 ダイキン工業株式会社 多段電動膨張弁及び冷凍装置
CN102252119A (zh) * 2010-05-21 2011-11-23 浙江三花股份有限公司 一种电动阀及包括该电动阀的热交换装置
JP2012047213A (ja) * 2010-08-25 2012-03-08 Saginomiya Seisakusho Inc 電動弁
CN202182593U (zh) * 2011-08-05 2012-04-04 株式会社鹭宫制作所 膨胀阀、热泵式制冷循环设备和空气处理机组

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2345306A (en) 1942-02-24 1944-03-28 Adel Prec Products Corp Fluid controlled valve
BE756932A (fr) * 1969-10-02 1971-04-01 Fischer Controls Cy Soupapes comportant notamment un dispositif reduisant l'intensite des bruits
EP0689015A1 (de) * 1994-06-21 1995-12-27 Staefa Control System Scs Ag Regelventil mit Stellantrieb
JPH08145507A (ja) 1994-11-24 1996-06-07 Sanyo Electric Co Ltd 冷媒流量制御弁及び冷媒流量制御弁を用いた冷凍装置
JP3937029B2 (ja) 1999-03-26 2007-06-27 株式会社鷺宮製作所 電動弁
US7104281B2 (en) * 2003-08-15 2006-09-12 Dresser, Inc. Fluid flow regulation
US8157184B2 (en) * 2008-05-29 2012-04-17 Kabushiki Kaisha Saginomiya Seisakusho Expansion valve, heat pump type refrigeration cycle apparatus, and air handling unit
US8157183B2 (en) 2008-05-29 2012-04-17 Kabushiki Kaisha Saginomiya Seisakusho Expansion valve, heat pump type refrigeration cycle apparatus, and air handling unit
US7854390B2 (en) 2008-05-29 2010-12-21 Kabushiki Kaisha Saginomiya Seisakusho Expansion valve, heat pump type refrigeration cycle apparatus, and air handling unit
JP3145048U (ja) 2008-07-11 2008-09-25 株式会社鷺宮製作所 電動膨張弁及び冷凍サイクル
CN201318457Y (zh) 2008-08-29 2009-09-30 王学军 一种直通式三阀片防跑水自闭水阀
CN201318475Y (zh) * 2008-12-11 2009-09-30 孙光锋 一种梭阀
CN101956830B (zh) * 2009-07-17 2013-06-12 浙江三花股份有限公司 电子膨胀阀
CN102042416B (zh) * 2009-10-09 2012-11-21 浙江三花股份有限公司 电子膨胀阀

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100552942B1 (ko) * 2002-12-02 2006-02-22 가부시기가이샤 후지고오키 전동 밸브
JP4285155B2 (ja) * 2003-08-27 2009-06-24 ダイキン工業株式会社 多段電動膨張弁及び冷凍装置
CN200968423Y (zh) * 2006-11-16 2007-10-31 鞍山电磁阀有限责任公司 智能型套筒式高温高压电磁阀
CN102252119A (zh) * 2010-05-21 2011-11-23 浙江三花股份有限公司 一种电动阀及包括该电动阀的热交换装置
JP2012047213A (ja) * 2010-08-25 2012-03-08 Saginomiya Seisakusho Inc 電動弁
CN202182593U (zh) * 2011-08-05 2012-04-04 株式会社鹭宫制作所 膨胀阀、热泵式制冷循环设备和空气处理机组

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111734883A (zh) * 2019-03-25 2020-10-02 株式会社鹭宫制作所 温度式膨胀阀及具备该温度式膨胀阀的冷冻循环系统
CN111734883B (zh) * 2019-03-25 2022-03-18 株式会社鹭宫制作所 温度式膨胀阀及具备该温度式膨胀阀的冷冻循环系统

Also Published As

Publication number Publication date
CN103453699A (zh) 2013-12-18
CN103453699B (zh) 2016-08-10
US20150129067A1 (en) 2015-05-14
US9341399B2 (en) 2016-05-17

Similar Documents

Publication Publication Date Title
WO2013177865A1 (zh) 一种电子膨胀阀
WO2013166791A1 (zh) 一种电子膨胀阀
WO2013189120A1 (zh) 一种电子膨胀阀
WO2013170542A1 (zh) 一种电子膨胀阀
WO2013166790A1 (zh) 一种电子膨胀阀
US11852263B2 (en) Fluid management assembly
JP6194157B2 (ja) 電動弁
US20180258927A1 (en) Electronic expansion valve
CN103511636B (zh) 一种电子膨胀阀
WO2018121412A1 (zh) 膨胀开关阀
US9631850B2 (en) Thermal expansion valve with one-way control function
CN112129000B (zh) 热管理系统
CN211779163U (zh) 一种流路切换装置
CN210851949U (zh) 组合阀、热管理组件及热管理系统
JP2010249247A (ja) 電動弁及びそれが用いられた冷凍サイクル
WO2018121418A1 (zh) 膨胀开关阀
JP6194403B2 (ja) 電動弁
CN106322862B (zh) 流量控制阀及换热系统
CN114279112B (zh) 节流阀及换热系统
WO2018176284A1 (zh) 空调器
CN201233783Y (zh) 电磁阀线圈
CN112757863A (zh) 流体管理组件、热管理组件及热管理系统
CN115727165A (zh) 一种换向阀
CN112443678A (zh) 一种流路切换装置
WO2013139187A1 (zh) 一种双向电磁阀

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: 12877630

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 14401484

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12877630

Country of ref document: EP

Kind code of ref document: A1