WO2013189120A1 - 一种电子膨胀阀 - Google Patents

一种电子膨胀阀 Download PDF

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Publication number
WO2013189120A1
WO2013189120A1 PCT/CN2012/079936 CN2012079936W WO2013189120A1 WO 2013189120 A1 WO2013189120 A1 WO 2013189120A1 CN 2012079936 W CN2012079936 W CN 2012079936W WO 2013189120 A1 WO2013189120 A1 WO 2013189120A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
electronic expansion
hole
piston
expansion valve
Prior art date
Application number
PCT/CN2012/079936
Other languages
English (en)
French (fr)
Inventor
詹才意
袁泽
魏先让
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 US14/408,284 priority Critical patent/US9810461B2/en
Publication of WO2013189120A1 publication Critical patent/WO2013189120A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—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
    • F16K15/00—Check valves
    • F16K15/18—Check valves with actuating mechanism; Combined check valves and actuated valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/325—Expansion valves having two or more valve members
    • 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
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87177—With bypass

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. 2010-249246 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.
  • a valve core seat 22 is fixed in the valve seat 20, and a valve port 22a is disposed on the valve core seat 22.
  • a plurality of small holes 72 are further distributed around the valve port 22a, and the inlet pipe socket 45 is disposed.
  • the main valve body is formed by screwing with the valve seat 20, the auxiliary valve chamber is formed between the valve seat 20 and the inlet socket 45, and the check valve chamber 60 is provided in the auxiliary valve chamber.
  • valve port 22a adjusts the opening of the valve port 22a to adjust the flow rate of the system.
  • the refrigerant flows in the opposite direction (that is, from the outlet nozzle 16 to the inlet nozzle 17)
  • the outlet nozzle 16 is high pressure
  • the inlet nozzle 17 is low pressure
  • the one-way spool 60 is pushed away from the valve core seat 22, and the small hole 72 is opened, the flow rate Most of them flow through the small holes 72. Since the small holes 72 can be provided in plurality, the total flow area is large, so that the flow resistance of the product can be greatly reduced.
  • the one-way spool 60 is provided at the lower portion of the spool seat 22, and the valve needle 24 is respectively disposed on both sides of the spool seat 22, and the upward impact of the refrigerant is caused when the refrigerant flows in the forward direction.
  • the buffer spring built in the valve needle 24 has a large spring force to ensure that the valve needle 24 is sealed under high pressure conditions, and the increase of the spring force will bring a series of problems, which will increase the valve needle 24 Difficult to turn, will increase the volume of the product, in general, the spring can be designed to withstand 2.5MPa of cold The pressure of the medium is still quite good.
  • the product of this structure is difficult to keep sealed under the pressure of 3.5MPa.
  • the one-way spool 60 is mounted on the lower portion of the spool seat 22, and requires a certain stroke of the one-way spool 60, which inevitably requires a larger installation space in the lower portion of the spool seat 22, which increases the shaft of the valve body. To the height.
  • valve seat 20 has a sufficiently large diameter which in turn causes the valve seat 20 to have a larger radial dimension.
  • 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 ensure that the valve needle member can easily seal the valve spool valve when the refrigerant is flowing in a high pressure state, and the valve needle member is prevented from being The high pressure refrigerant is opened; on the other hand, the axial and radial dimensions of the valve seat can be reduced, and the flow resistance in the reverse flow can be reduced.
  • the present invention provides an electronic expansion valve including a valve seat, the valve seat is provided with a valve cavity, a valve core seat is fixed in the valve cavity, and the valve core seat is provided with a valve core valve port and a side a passage and a piston member that opens and closes the bypass through hole in an axial direction;
  • the electronic expansion valve further includes a cross pipe as an inlet pipe and a vertical pipe as an outlet pipe;
  • the piston member and the valve needle member are on the same side of the spool seat such that when the refrigerant flows in the forward direction, the piston member closes the bypass through hole, and the refrigerant flows to the end of the vertical pipe through the spool valve port
  • the valve needle member moves in the axial direction to adjust the opening degree of the spool valve port; when the refrigerant flows in the reverse direction, the piston member moves upward in the axial direction to open the bypass through hole, and the refrigerant passes through the bypass through hole Flow to the end of the pipe.
  • the wide core seat and the wide seat are separated structures, and the wide core seat is fixedly connected to the inner wall of the valve seat.
  • the valve core seat includes a body portion and a sleeve guide portion; the spool valve port and the bypass through hole are formed on the body portion, and a lower end of the sleeve guide portion surrounds the valve Core valve port, The valve needle member is guided into an inner bore of the sleeve guide to engage the spool valve port.
  • the piston member is provided with a central hole, the piston member being axially movably sleeved on the outer wall of the sleeve guide with its central hole.
  • the inner wall of the central hole and the outer wall of the sleeve guiding portion are provided with positioning grooves extending along the axial direction thereof, and the other is provided with a positioning position capable of sliding in the positioning groove Raised portion.
  • the piston member cuts a piece toward a side of the cross tube to form a notch.
  • the side wall of the sleeve guiding portion is provided with a side wall through hole communicating with the inner hole and the wide cavity.
  • the piston member includes a piston body portion and a piston guide portion that protrudes upward along the piston body portion, the center hole penetrating the piston body portion and the piston guide portion.
  • a side wall of the piston guiding portion is further provided with a piston side hole which is aligned with the through hole of the side wall.
  • the electronic expansion valve further includes a driving member that drives the valve needle member to move in the axial direction, and the driving member includes a screw rod and a nut threadedly engaged with the screw rod;
  • a lower portion of the nut is provided with a guiding hole, and an upper portion of the sleeve guiding portion is guided and fitted with the outer wall thereof.
  • a compressed elastic member is disposed between the top wall of the piston member and the nut.
  • the piston member of the electronic expansion valve provided by the present invention and the valve needle member are on the same side of the valve core seat, so that the piston member closes the side when the refrigerant flows in the forward direction.
  • the bypass through hole is opened, and the refrigerant flows to the one end of the transverse pipe through the bypass through hole.
  • the refrigerant When the refrigerant flows in the forward direction, the refrigerant enters through the cross pipe and flows out from the vertical pipe. Therefore, one end of the cross pipe is a high pressure zone, and one end of the pipe is a low pressure zone. Under the action of the differential pressure of the system, the piston component moves downward, thereby closing. Bypassing the through hole; Then, driven by the driving member of the electronic expansion valve, the valve needle member moves up and down in the axial direction, thereby adjusting the opening degree of the valve port of the spool to achieve the purpose of adjusting the flow rate of the refrigerant.
  • the refrigerant When the refrigerant flows in the reverse direction, the refrigerant enters through the vertical pipe and flows out from the cross pipe, so the vertical pipe One end is a high pressure zone, and one end of the cross pipe is a low pressure zone. Under the action of the differential pressure of the system, the piston component moves upward to open the bypass through hole, and the refrigerant flows to the end of the cross pipe through the bypass through hole, thereby achieving the purpose of reverse conduction. .
  • the piston member and the valve needle member are on the same side of the valve body seat, that is, the piston member and the valve needle member are both on the upper side of the valve body seat, not respectively disposed on both sides, thus
  • the valve needle member is not subjected to the impact force of the high pressure refrigerant at one end of the cross tube, so the spring force of the buffer spring provided in the valve needle member can be set small, and the valve needle member is easy under the high pressure state of the refrigerant.
  • the spool valve port is sealed without being opened, and the seal can be maintained at a pressure of 3.5 MPa.
  • the stroke of the piston member fully utilizes the valve chamber above the spool seat, thereby eliminating the inlet nozzle in the background art.
  • the structural design of the seat and the secondary valve chamber thus reduces the axial dimension of the valve seat.
  • the refrigerant can directly enter one end of the cross pipe, thereby eliminating the design of the bypass flow path in the prior art, thereby reducing the flow resistance and, at the same time, eliminating the need for design bypass. The flow path, and thus the radial dimension of the valve seat, is also reduced.
  • the electronic expansion valve provided by the invention can ensure that the valve needle component can easily seal the valve spool valve when the refrigerant is flowing forward in a high pressure state, and the valve needle component can be prevented from being opened by the high pressure refrigerant; Reduce the axial and radial dimensions of the seat and reduce flow resistance during reverse flow.
  • 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
  • Figure 5 is a schematic view showing the structure of the electronic expansion valve in the reverse flow of the refrigerant in the first embodiment of the present invention
  • Figure 6 is a schematic structural view of the valve core seat of the electronic expansion valve of Figures 4 and 5;
  • Figure 7 is a cross-sectional view of the spool seat of Figure 6;
  • Figure 8 is a schematic view showing the structure of the piston member of the electronic expansion valve of Figures 4 and 5;
  • Figure 9 is a schematic view showing the structure of the electronic expansion valve in the forward flow of the refrigerant in the second embodiment of the present invention.
  • Figure 10 is a schematic view showing the structure of an electronic expansion valve in a reverse flow of a refrigerant in a second embodiment of the present invention.
  • Figure 11 is a schematic view showing the structure of the piston member of the electronic expansion valve of Figures 9 and 10;
  • Figure 12 is a plan view of the piston member of Figure 11.
  • the correspondence between the reference numerals and the component names in FIGS. 1 to 3 is:
  • valve seat 20 valve seat; 22 valve seat; 22a valve port; 72 small hole; 45 inlet socket; 60 check valve core; 17 inlet nozzle; 16 outlet nozzle; 24 valve needle; 70 bypass flow path.
  • the correspondence between the reference numerals and the component names in FIGS. 4 to 12 is: 1 valve seat; 11 valve moon space;
  • the core of the present invention is to provide an electronic expansion valve, the structural design of which can ensure that the valve needle member can easily seal the valve spool when the refrigerant is flowing in a high pressure state. Avoiding the needle member being pushed open by the high pressure refrigerant; on the other hand, it can reduce the axial and radial dimensions of the seat and reduce the flow resistance during reverse flow.
  • 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 a diagram showing the reverse flow of the electronic expansion valve in the refrigerant in the first embodiment of the present invention
  • Schematic diagram of the time
  • the electronic expansion valve provided by the present invention comprises a valve seat 1 which is provided with a valve chamber 11 in which a valve is fixed.
  • the core seat 2, the spool seat 2 is provided with a spool valve port 211 and a bypass through hole 212;
  • the electronic expansion valve further includes a valve needle member 3 that moves in the axial direction to cooperate with the spool valve port 211, and moves in the axial direction
  • the piston member 4 of the bypass through hole 212 is opened and closed;
  • the electronic expansion valve further includes a cross pipe 51 as an inlet pipe and a riser pipe 52 as an outlet pipe.
  • the piston member 4 and the valve needle member 3 are on the same side of the valve body seat 2, so that the piston member 4 closes the bypass through hole 212 when the refrigerant flows in the forward direction.
  • the refrigerant flows through the spool valve port 211 to the end of the vertical pipe 52, and the needle member 3 moves in the axial direction to adjust the opening degree of the spool valve port 211; when the refrigerant flows in the reverse direction, the piston member 4 moves upward in the axial direction to open the bypass passage.
  • the hole 212 flows through the bypass through hole 212 to the end of the cross pipe 51.
  • the refrigerant flows in the forward direction, the refrigerant enters through the cross pipe 51 and flows out from the vertical pipe 52. Therefore, the cross pipe 51 is a high pressure zone, and the pipe 52 is a low pressure zone.
  • the piston component 4 moves downward to close the bypass through hole 212; then, under the driving of the driving member of the electronic expansion valve, the needle member 3 moves up and down in the axial direction, thereby adjusting the opening degree of the spool valve port 211, thereby realizing the refrigerant The purpose of the flow adjustment.
  • the refrigerant flows in the reverse direction
  • the refrigerant enters through the vertical pipe 52 and flows out through the cross pipe 51. Therefore, the end of the vertical pipe 52 is a high pressure zone, and the end of the cross pipe 51 is a low pressure zone.
  • the piston component 4 The upward movement opens the bypass through hole 212, and the refrigerant flows to the end of the cross pipe 51 via the bypass through hole 212, thereby achieving the purpose of reverse conduction.
  • the piston member 4 and the needle member 3 are on the same side of the valve body seat 2, that is, the piston member 4 and the valve needle member 3 are both on the upper side of the valve body seat 2, not on both sides, Therefore, when the refrigerant flows in the forward direction, the valve needle member 3 is not subjected to the impact force of the cross-tube 51-end high-pressure refrigerant, so that the spring force of the buffer spring provided in the valve needle member 3 can be set small, and the high pressure in the refrigerant In the state, the needle member 3 is easy to seal the spool valve port 211 without being opened, and can be kept sealed at a pressure of 3.5 MPa.
  • the piston member 4 since the piston member 4 is on the upper side of the spool seat 2, that is, the piston member 4 is provided in the valve chamber 11, the stroke of the piston member 4 makes full use of the valve chamber 11 above the spool seat 2,
  • the structural design of the inlet and the secondary valve chamber in the background art is eliminated, so that the axial dimension of the valve seat 1 is reduced.
  • the refrigerant can directly enter the cross-section of the cross-section tube 51, eliminating the design of the bypass flow path in the prior art, thereby reducing the flow resistance and, at the same time,
  • the bypass flow path is designed such that the radial dimension of the valve seat 1 is also reduced.
  • the electronic expansion valve provided by the present invention can ensure that the valve needle member 3 can easily seal the valve spool 211 when the refrigerant is flowing forward in a high pressure state, thereby preventing the valve needle member 3 from being opened by the high pressure refrigerant; It is possible to reduce the axial and radial dimensions of the valve seat 1 and to reduce the flow resistance in the reverse flow.
  • valve core seat 2 can be integrated with the valve seat 1, that is, the valve core seat is formed by machining in the interior of the valve seat 1. 2; of course, as shown in FIG. 4 and FIG. 5, the valve core seat 2 and the valve seat 1 may also be a separate structure, and the valve core seat 2 is fixedly connected to the inner wall of the valve seat 1, specifically, the valve core seat 2 It is welded to the inner wall of the valve seat 1 by its outer peripheral wall.
  • FIG. 6 is a structural schematic view of the valve core seat of the electronic expansion valve of FIG. 4 and FIG. 5.
  • FIG. 7 is a cross-sectional view of the valve core seat of FIG.
  • the spool seat 2 includes a body portion 21 and a sleeve guide portion 22; the spool valve port 211 and the bypass through hole 212 are opened on the body portion 21, and the lower end of the sleeve guide portion 22 is surrounded.
  • the spool valve port 211, the valve needle member 3 is guided into the inner bore of the sleeve guide portion 22 to cooperate with the spool valve port 211.
  • the inner hole of the sleeve guide 22 and the valve spool 211 can be integrally formed, so that a good coaxiality can be maintained between the two, and the needle member 3 is guided to the extension.
  • the valve needle member 3 can maintain a good coaxiality with the spool valve port 211, thereby providing excellent sealing performance. Further, the sleeve guide portion 22 can block the impact of the high-pressure refrigerant on the needle member 3, prevent eccentricity and radial chattering, and ensure the sealing performance.
  • the piston member 4 is provided with a center hole 41 which is axially movably fitted to the outer wall of the sleeve guide portion 22 with its center hole 41.
  • This structural design guides the axial movement of the piston member 4 to prevent it from deflecting, thereby ensuring the sealing performance.
  • the inner wall of the center hole 41 and the outer wall of the sleeve guide portion 22 are provided with positioning grooves 221 extending in the axial direction thereof, and the other is provided therein.
  • the positioning projection 411 that slides in the groove 221 is positioned.
  • the piston member 4 is cut toward the side of the cross pipe 51 to form a notch portion 42.
  • the notch portion 42 is designed to prevent the piston member 4 from interfering with the cross pipe 51.
  • the structural design of the positioning groove 221 and the positioning boss portion 411 can prevent the piston member 4 from rotating in the circumferential direction, thereby preventing the piston member 4 from being removed from the portion other than the notch portion 42 to the end of the cross tube 51. Thereby, interference with the cross tube 51 occurs.
  • the side wall of the sleeve guide portion 22 is provided with a side wall through hole 222 communicating with the inner hole and the valve chamber 11.
  • the refrigerant passes through the spool valve port 211, passes through the inner hole of the sleeve guide portion 22, passes through the side wall through hole 222, enters the valve chamber 11, and finally flows into the cross tube 51. end.
  • the electronic expansion valve further includes a driving member that drives the valve needle member 3 to move in the axial direction
  • the driving member includes a screw rod 61 and a nut 62 threadedly engaged with the screw rod 61;
  • a guide hole is formed in the lower portion, and an upper portion of the sleeve guide portion 22 is guided and fitted into the guide hole with an outer wall thereof.
  • the spool seat 2 is further guided by the nut 62, so that the coaxiality of the needle member 3 and the spool port 211 can be further improved to ensure the sealing performance between the two.
  • a compressed elastic member 7 is provided between the top wall of the piston member 4 and the nut 62.
  • the nut 62 is provided with a convex portion in the circumferential direction, and the upper end 4 of the compressed elastic member 7 is attached to the convex portion.
  • the present invention also provides a second embodiment. Specifically, please refer to Figure 9, Figure 10, and Figure
  • FIG. 9 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. 10 is a view showing the structure of the electronic expansion valve in the reverse flow of the refrigerant in the second embodiment of the present invention
  • Figure 11 is a schematic view showing the structure of the piston member of the electronic expansion valve of Figures 9 and 10
  • Figure 12 is a plan view of the piston member of Figure 11.
  • the structure of the electronic expansion valve is the same as that of the electronic expansion valve in the first embodiment described above, and thus will not be described again; the difference is that in the second In the embodiment, as shown in FIG. 11, the piston member 4 includes a piston body portion 43 and a piston guide portion 44 that protrudes upward along the piston body portion 43, and the center hole 41 penetrates the piston body portion 43 and the piston guide portion 44. Further, the side wall of the piston guide portion 44 is provided with a piston side hole 441 which is aligned with the side wall through hole 222.
  • the piston guide portion 44 is designed to guide the movement of the piston member 4 in the axial direction, so that the axial movement thereof is more stable and reliable, and the bypass through hole 212 can be opened and closed more reliably.

Abstract

一种电子膨胀阀，其活塞部件（4）与其阀针部件（3）处于阀芯座（2）的同一侧，以便冷媒正向流动时，所述活塞部件（4）关闭旁路通孔（212），冷媒经由该阀芯阀口（211）流向竖接管（52）一端，所述阀针部件（3）沿轴向运动调节所述阀芯阀口（211）的开度；冷媒逆向流动时，所述活塞部件（4）沿轴向上移开启所述旁路通孔（212），冷媒经由该旁路通孔（212）流向横接管（51）一端。该电子膨胀阀的结构设计一方面能够保证在冷媒正向流动高压状态下阀针部件能够易于密封阀芯阀口；另一方面能够减少阀座的轴向和径向尺寸。

Description

一种电子膨胀阀 本申请要求于 2012 年 06 月 20 日提交中国专利局、 申请号为 201210208265.1、 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 2010-249246" 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， 阀座 20内固定有阀芯座 22, 阀口 22a设置在阀 芯座 22上， 在阀口 22a的周边还分布了多个小孔 72, 进口接管座 45与阀 座 20螺纹连接形成主阀体， 阀座 20与进口接管座 45之间形成副阀室， 副 阀室中有单向阀芯 60, 在冷媒正向流动时 （亦即由进口接管 17流向出口 接管 16 ), 由于进口接管 17是高压， 出口接管 16是低压， 单向阀芯 60推 向阀芯座 22, 将小孔 72关闭， 这时阀针 24在驱动机构带动下接近或远离 阀口 22a, 调节阀口 22a的开度， 从而对系统流量的调节。 当冷媒逆向流 动时 （亦即由出口接管 16流向进口接管 17 ), 由于出口接管 16是高压， 进口接管 17是低压， 单向阀芯 60推离阀芯座 22, 将小孔 72打开， 流量 大部分从小孔 72中流过， 由于小孔 72可设置多个， 流通面积总和较大， 因此可大大减小产品的流动阻力。
然而， 上述现有技术中的电子膨胀阀具有如下缺陷：
第一， 在上述结构中， 单向阀芯 60设于阀芯座 22的下部， 与阀针 24 分别设于阀芯座 22的两侧，在冷媒正向流动时， 由于冷媒向上的冲击力较 大， 这样要求阀针 24内设的緩冲弹簧具有较大的弹簧力才能保证阀针 24 在高压条件下密封， 而弹簧力增大后会带来一系列问题， 会加大阀针 24 转动困难， 会增加产品体积， 一般来说， 弹簧能够设计经受 2.5MPa的冷 媒压力保持密封已相当不错， 这种结构的产品很难在 3.5MPa 的冷媒压力 下保持密封。
第二， 单向阀芯 60安装在阀芯座 22的下部， 同时要求单向阀芯 60 有一定的行程， 必然要求阀芯座 22的下部有较大的安装空间，会增加阀体 的轴向高度。
第三， 由于单向阀芯 60需设置旁通流路 70, 逆向流动时冷媒需要经 过该旁通流路 70, 因而导致逆向流阻较大； 在此基础上， 为了降低逆向流 阻， 需要阀座 20有足够大的直径， 因而又会导致阀座 20径向上的尺寸较 大。 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， 该电子膨胀阀的结 构设计一方面能够保证在冷媒正向流动高压状态下阀针部件能够易于密封 阀芯阀口， 避免阀针部件被高压冷媒顶开； 另一方面能够减少阀座的轴向 和径向尺寸， 并降低逆向流动时的流阻。
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， 该阀 座设有阀腔， 该阀腔内固定有阀芯座， 所述阀芯座设有阀芯阀口和旁路通 及沿轴向运动而开启和关闭所述旁路通孔的活塞部件； 所述电子膨胀阀还 包括作为进口接管的横接管和作为出口接管的竖接管；
所述活塞部件与所述阀针部件处于所述阀芯座的同一侧， 以便冷媒正 向流动时， 所述活塞部件关闭所述旁路通孔， 冷媒经由该阀芯阀口流向竖 接管一端， 所述阀针部件沿轴向运动调节所述阀芯阀口的开度； 冷媒逆向 流动时， 所述活塞部件沿轴向上移开启所述旁路通孔， 冷媒经由该旁路通 孔流向横接管一端。
优选地， 所述阔芯座与所述阔座为分体结构， 所述阔芯座固定连接于 所述阀座的内壁上。
优选地， 所述阀芯座包括本体部及套筒导向部； 所述阀芯阀口和所述 旁路通孔开设于所述本体部上，所述套筒导向部的下端包围所述阀芯阀口， 所述阀针部件导向伸入该套筒导向部的内孔中与所述阀芯阀口配合。
优选地， 所述活塞部件设有中心孔， 该活塞部件以其中心孔可沿轴向 活动套于所述套筒导向部的外壁上。
优选地， 所述中心孔的内壁上与所述套筒导向部的外壁上， 一者设有 沿其轴向延伸的定位凹槽， 另一者设有可在该定位凹槽中滑动的定位凸起 部。
优选地， 所述活塞部件朝向所述横接管的一侧切去一块形成缺口部。 优选地， 所述套筒导向部的侧壁上开设有连通其内孔与所述阔腔的侧 壁通孔。
优选地， 所述活塞部件包括活塞本体部和沿该活塞本体部向上凸出的 活塞导向部， 所述中心孔贯穿所述活塞本体部和所述活塞导向部。
优选地， 所述活塞导向部的侧壁上进一步设有与所述侧壁通孔对位的 活塞侧孔。
优选地， 所述电子膨胀阀还包括驱动所述阀针部件沿轴向运动的驱动 部件， 所述驱动部件包括丝杆及与该丝杆螺纹配合的螺母；
所述螺母的下部开设有导向孔， 所述套筒导向部的上部以其外壁导向 配合于所述导向孔中。
优选地，所述活塞部件的顶壁与所述螺母之间设有被压缩的弹性部件。 在现有技术的基础上， 本发明所提供的电子膨胀阀的活塞部件与所述 阀针部件处于所述阀芯座的同一侧， 以便冷媒正向流动时， 所述活塞部件 关闭所述旁路通孔， 冷媒经由该阀芯阀口流向竖接管一端， 所述阀针部件 沿轴向运动调节所述阀芯阀口的开度； 冷媒逆向流动时， 所述活塞部件沿 轴向上移开启所述旁路通孔， 冷媒经由该旁路通孔流向横接管一端。
当冷媒正向流动时， 冷媒由横接管进入， 由竖接管流出， 因而横接管 一端是高压区， 竖接管一端是低压区， 在系统压差力的作用下， 活塞部件 向下运动， 从而关闭旁路通孔； 然后， 电子膨胀阀的驱动部件的驱动下， 阀针部件沿轴向上下运动， 从而调节阀芯阀口的开度， 实现对冷媒流量进 行调节的目的。
当冷媒逆向流动时， 冷媒由竖接管进入， 由横接管流出， 因而竖接管 一端是高压区， 横接管一端是低压区， 在系统压差力的作用下， 活塞部件 向上运动开启旁路通孔， 冷媒经由该旁路通孔流向横接管一端， 从而实现 逆向导通的目的。
在上述结构中， 由于活塞部件与所述阀针部件处于所述阀芯座的同一 侧， 亦即活塞部件和阀针部件均处于阀芯座的上侧， 不是分别设于两侧， 因而当冷媒正向流动时， 阀针部件不会受到横接管一端高压力冷媒的冲击 力， 因而该阀针部件内设的緩冲弹簧的弹簧力可以设置较小， 在冷媒高压 状态下阀针部件易于密封阀芯阀口而不被顶开， 在 3.5MPa的冷媒压力下 也能保持密封。
此外， 在上述结构中， 由于活塞部件处于阀芯座的上侧， 亦即活塞部 件设于阀腔中， 活塞部件的行程充分利用阀芯座上方的阀腔， 因而省却了 背景技术中进口接管座和副阀室的结构设计， 因而使得阀座的轴向尺寸得 以减小。 此外， 在本发明中， 活塞部件被顶开后， 冷媒便可直接进入横接 管一端， 省却了现有技术中旁通流路的设计， 因而可以减少流阻， 同时， 由于不需要设计旁通流路， 因而阀座的径向尺寸也得以减小。
综上所述， 本发明所提供的电子膨胀阀一方面能够保证在冷媒正向流 动高压状态下阀针部件能够易于密封阀芯阀口， 避免阀针部件被高压冷媒 顶开； 另一方面能够减少阀座的轴向和径向尺寸， 并降低逆向流动时的流 阻。 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为本发明第一种实施例中电子膨胀阀在冷媒逆向流动时的结构示 意图；
图 6为图 4和图 5中电子膨胀阀的阀芯座的结构示意图； 图 7为图 6中阀芯座的剖视图；
图 8为图 4和图 5中电子膨胀阀的活塞部件的结构示意图；
图 9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 10 为本发明第二种实施例中电子膨胀阀在冷媒逆向流动时的结构 示意图；
图 11为图 9和图 10中电子膨胀阀的活塞部件的结构示意图； 图 12为图 11中活塞部件的俯视图。 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：
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； 7'5第二电子膨胀阀； 7'6第二单向阀； 77室内换热器； 7'8压缩机；
20阀座； 22阀芯座； 22a阀口； 72小孔； 45进口接管座； 60单向阀 芯； 17进口接管； 16出口接管； 24阀针； 70旁通流路。 其中， 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阀月空；
2阀芯座； 21本体部； 211阀芯阀口； 212旁路通孔； 22套筒导向部； 221定位凹槽； 222侧壁通孔；
3阀针部件；
4活塞部件； 41中心孔； 411定位凸起部； 42缺口部； 43活塞本体部； 44活塞导向部； 441活塞侧孔；
51横接管； 52竖接管；
61丝杆； 62螺母；
7弹性部件。 具体实施方式
本发明的核心为提供一种电子膨胀阀， 该电子膨胀阀的结构设计一方 面能够保证在冷媒正向流动高压状态下阀针部件能够易于密封阀芯阀口， 避免阀针部件被高压冷媒顶开；另一方面能够减少阀座的轴向和径向尺寸， 并降低逆向流动时的流阻。
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和图 5 , 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为本发明第一种实施例中电子膨胀阀在冷 媒逆向流动时的结构示意图。
在本发明第一种实施例中， 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 , 该阀座 1设有阀腔 11 , 该阀腔 11内固定有阀芯座 2, 阀芯座 2设有阀芯阀口 211和旁路通孔 212; 电子膨胀阀还包括沿轴向运 动而与阀芯阀口 211配合的阀针部件 3、 及沿轴向运动而开启和关闭旁路 通孔 212的活塞部件 4; 电子膨胀阀还包括作为进口接管的横接管 51和作 为出口接管的竖接管 52。
在上述结构的基础上， 如图 4和图 5所示， 活塞部件 4与阀针部件 3 处于阀芯座 2的同一侧， 以便冷媒正向流动时， 活塞部件 4关闭旁路通孔 212, 冷媒经由该阀芯阀口 211流向竖接管 52—端， 阀针部件 3沿轴向运 动调节阀芯阀口 211的开度； 冷媒逆向流动时， 活塞部件 4沿轴向上移开 启旁路通孔 212, 冷媒经由该旁路通孔 212流向横接管 51—端。
当冷媒正向流动时， 冷媒由横接管 51进入， 由竖接管 52流出， 因而 横接管 51—端是高压区， 竖接管 52—端是低压区， 在系统压差力的作用 下， 活塞部件 4向下运动， 从而关闭旁路通孔 212; 然后， 在电子膨胀阀 的驱动部件的驱动下，阀针部件 3沿轴向上下运动，从而调节阀芯阀口 211 的开度， 实现对冷媒流量进行调节的目的。
当冷媒逆向流动时， 冷媒由竖接管 52进入， 由横接管 51流出， 因而 竖接管 52—端是高压区， 横接管 51—端是低压区， 在系统压差力的作用 下， 活塞部件 4向上运动开启旁路通孔 212, 冷媒经由该旁路通孔 212流 向横接管 51—端， 从而实现逆向导通的目的。
在上述结构中，由于活塞部件 4与阀针部件 3处于阀芯座 2的同一侧 , 亦即活塞部件 4和阀针部件 3均处于阀芯座 2的上侧，不是分别设于两侧， 因而当冷媒正向流动时，阀针部件 3不会受到横接管 51—端高压力冷媒的 冲击力， 因而该阀针部件 3内设的緩冲弹簧的弹簧力可以设置较小， 在冷 媒高压状态下阀针部件 3 易于密封阀芯阀口 211 而不被顶开， 在 3.5MPa 的冷媒压力下也能保持密封。
此外， 在上述结构中， 由于活塞部件 4处于阀芯座 2的上侧， 亦即活 塞部件 4设于阀腔 11中，活塞部件 4的行程充分利用阀芯座 2上方的阀腔 11 , 因而省却了背景技术中进口接管座和副阀室的结构设计， 因而使得阀 座 1的轴向尺寸得以减小。 此外， 在本发明中， 活塞部件 4被顶开后， 冷 媒便可直接进入横接管 51—端，省却了现有技术中旁通流路的设计， 因而 可以减少流阻， 同时， 由于不需要设计旁通流路， 因而阀座 1的径向尺寸 也得以减小。
综上， 本发明所提供的电子膨胀阀一方面能够保证在冷媒正向流动高 压状态下阀针部件 3能够易于密封阀芯阀口 211 , 避免阀针部件 3被高压 冷媒顶开； 另一方面能够减少阀座 1的轴向和径向尺寸， 并降低逆向流动 时的流阻。
需要说明的是， 在本发明中， 如同于背景技术中的阀芯座 2结构， 阀 芯座 2可以与阀座 1为一体结构， 亦即在阀座 1的内部通过车加工形成阀 芯座 2; 当然， 如图 4和图 5所示， 阀芯座 2与阀座 1也可以为分体结构， 阀芯座 2固定连接于阀座 1的内壁上， 具体地， 该阀芯座 2通过其外周壁 焊接于阀座 1的内壁上。
在上述结构的基础上， 可以对阀芯座 2和活塞部件 4的具体结构作出 设计。 比如， 请参考图 6、 图 7和图 8, 图 6为图 4和图 5中电子膨胀阀的 阀芯座的结构示意图； 图 7为图 6中阀芯座的剖视图； 图 8为图 4和图 5 中电子膨胀阀的活塞部件的结构示意图。
如图 6和图 7所示， 阀芯座 2包括本体部 21及套筒导向部 22; 阀芯 阀口 211和旁路通孔 212开设于本体部 21上， 套筒导向部 22的下端包围 阀芯阀口 211 , 阀针部件 3导向伸入该套筒导向部 22的内孔中与阀芯阀口 211配合。 在该种结构设计中， 套筒导向部 22的内孔与阀芯阀口 211可以 一体加工形成， 因而二者之间能够保持较好的同轴度， 阀针部件 3导向伸 入套筒导向部 22的内孔中，因而阀针部件 3可以与阀芯阀口 211保持较好 的同轴度， 进而具有优良的密封性能。 此外， 套筒导向部 22还可以阻挡高 压冷媒对阀针部件 3的冲击， 防止其发生偏心和径向颤动， 保证密封性能 的发挥。
进一步地， 如图 8所示， 活塞部件 4设有中心孔 41 , 该活塞部件 4以 其中心孔 41可沿轴向活动套于套筒导向部 22的外壁上。 该种结构设计可 以对活塞部件 4的轴向运动进行导向， 防止其发生偏斜， 从而保证密封性 能的发挥。
此外， 如图 6和图 8所示， 中心孔 41的内壁上与套筒导向部 22的外 壁上， 一者设有沿其轴向延伸的定位凹槽 221 , 另一者设有可在该定位凹 槽 221中滑动的定位凸起部 411。 并且， 活塞部件 4朝向横接管 51的一侧 切去一块形成缺口部 42。
在上述结构中， 该缺口部 42的设计可以防止活塞部件 4与横接管 51 发生干涉。 此外， 定位凹槽 221和定位凸起部 411的结构设计， 可以防止 活塞部件 4沿周向发生转动，因而可以防止活塞部件 4除去缺口部 42之外 的其他部位转到横接管 51—端， 从而与横接管 51发生干涉。
进一步地，如图 6和图 7所示，套筒导向部 22的侧壁上开设有连通其 内孔与阀腔 11的侧壁通孔 222。 在该种结构中， 当冷媒逆向流动时， 冷媒 经过阀芯阀口 211 , 经过套筒导向部 22的内孔， 再经过侧壁通孔 222, 进 入阀腔 11中， 最后流入横接管 51—端。
此外， 如图 4和图 5所示， 电子膨胀阀还包括驱动阀针部件 3沿轴向 运动的驱动部件，驱动部件包括丝杆 61及与该丝杆 61螺纹配合的螺母 62; 螺母 62的下部开设有导向孔， 套筒导向部 22的上部以其外壁导向配合于 导向孔中。 在该种结构设计中， 阀芯座 2进一步由螺母 62导向支撑， 因而 能够进一步提高阀针部件 3与阀芯阀口 211的同轴度， 保证二者之间的密 封性能。
进一步地，如图 4和图 5所示， 活塞部件 4的顶壁与螺母 62之间设有 被压缩的弹性部件 7。 具体地， 螺母 62的周向设有凸起部， 该被压缩的弹 性部件 7的上端 4氏接于该凸起部上。 当冷媒由逆向流动转为正向流动时， 该弹性部件 7的设计可以使得活塞部件 4复位， 关闭旁路通孔 212。
此外， 本发明还提供第二种实施例。 具体地， 请参考图 9、 图 10、 图
11和图 12,图 9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 10为本发明第二种实施例中电子膨胀阀在冷媒逆向流动时 的结构示意图； 图 11为图 9和图 10中电子膨胀阀的活塞部件的结构示意 图； 图 12为图 11中活塞部件的俯视图。
在该第二种实施例中， 电子膨胀阀的结构与上文介绍的第一种实施例 中的电子膨胀阀的结构相同， 因而在此不再赘述； 所不同的是， 在该第二 种实施例中， 如图 11所示， 活塞部件 4包括活塞本体部 43和沿该活塞本 体部 43向上凸出的活塞导向部 44, 中心孔 41贯穿活塞本体部 43和活塞 导向部 44。 活塞导向部 44的侧壁上进一步设有与侧壁通孔 222对位的活 塞侧孔 441。
在上述结构中，活塞导向部 44的设计可以对活塞部件 4在轴向上的运 动进行导向， 使其沿轴向的运动更加平稳可靠， 进而能够更加可靠地开启 和关闭旁路通孔 212。
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), 该阀座（ 1 )设有阀腔（ 11 ), 该 阀腔（ 11 ) 内固定有阀芯座（ 2 ), 所述阀芯座（ 2 )设有阀芯阀口 （ 211 ) (211 ) 配合的阀针部件 （3)、 及沿轴向运动而开启和关闭所述旁路通孔 ( 212 )的活塞部件（ 4 );所述电子膨胀阀还包括作为进口接管的横接管（ 51 ) 和作为出口接管的竖接管 （52); 其特征在于，
所述活塞部件（4)与所述阀针部件（3)处于所述阀芯座（2)的同一 侧， 以便冷媒正向流动时， 所述活塞部件（4) 关闭所述旁路通孔（212), 冷媒经由该阀芯阀口 （211) 流向竖接管 （52)—端， 所述阀针部件 （3) 沿轴向运动调节所述阀芯阀口 （211 )的开度； 冷媒逆向流动时， 所述活塞 部件（ 4 )沿轴向上移开启所述旁路通孔（ 212 ),冷媒经由该旁路通孔（ 212 ) 流向横接管 （51 )一端。
2、 如权利要求 1所述的电子膨胀阀， 其特征在于， 所述阀芯座（2) 与所述阀座（1) 为分体结构， 所述阀芯座（2) 固定连接于所述阀座（1) 的内壁上。
3、 如权利要求 2所述的电子膨胀阀， 其特征在于， 所述阀芯座（2) 包括本体部 （21)及套筒导向部 （22); 所述阀芯阀口 （211)和所述旁路 通孔（212)开设于所述本体部（21 )上， 所述套筒导向部（22)的下端包 围所述阀芯阀口 （211), 所述阀针部件 （3)导向伸入该套筒导向部 （22) 的内孔中与所述阀芯阀口 （ 211 ) 配合。
4、 如权利要求 3所述的电子膨胀阀， 其特征在于， 所述活塞部件（4) 设有中心孔（41), 该活塞部件 （4) 以其中心孔（41)可沿轴向活动套于 所述套筒导向部 （22) 的外壁上。
5、 如权利要求 4所述的电子膨胀阀， 其特征在于， 所述中心孔（41) 的内壁上与所述套筒导向部 （22) 的外壁上， 一者设有沿其轴向延伸的定 位凹槽 （221 ), 另一者设有可在该定位凹槽 （221 ) 中滑动的定位凸起部 (411)。
6、 如权利要求 5所述的电子膨胀阀， 其特征在于， 所述活塞部件（4) 朝向所述横接管 （51) 的一侧切去一块形成缺口部 （42)。
7、如权利要求 3所述的电子膨胀阀，其特征在于，所述套筒导向部（ 22 ) 的侧壁上开设有连通其内孔与所述阀腔（11) 的侧壁通孔（222)。
8、 如权利要求 3所述的电子膨胀阀， 其特征在于， 所述活塞部件（4) 包括活塞本体部（ 43 )和沿该活塞本体部（ 43 )向上凸出的活塞导向部（ 44 ) , 所述中心孔（41 )贯穿所述活塞本体部 （43)和所述活塞导向部 （44)。
9、如权利要求 8所述的电子膨胀阀，其特征在于，所述活塞导向部（ 44 ) 的侧壁上进一步设有与所述侧壁通孔（222)对位的活塞侧孔（441)。
10、 如权利要求 3至 9任一项所述的电子膨胀阀， 其特征在于， 所述 电子膨胀阀还包括驱动所述阀针部件（ 3 )沿轴向运动的驱动部件， 所述驱 动部件包括丝杆（61)及与该丝杆（61 )螺纹配合的螺母（62);
所述螺母（62) 的下部开设有导向孔， 所述套筒导向部 （22) 的上部 以其外壁导向配合于所述导向孔中。
11、如权利要求 10所述的电子膨胀阀，其特征在于，所述活塞部件（4) 的顶壁与所述螺母（ 62 )之间设有被压缩的弹性部件（ 7 )。
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