WO2014089953A1 - 电子膨胀阀 - Google Patents

电子膨胀阀 Download PDF

Info

Publication number
WO2014089953A1
WO2014089953A1 PCT/CN2013/076411 CN2013076411W WO2014089953A1 WO 2014089953 A1 WO2014089953 A1 WO 2014089953A1 CN 2013076411 W CN2013076411 W CN 2013076411W WO 2014089953 A1 WO2014089953 A1 WO 2014089953A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
valve stem
seat
electronic expansion
stem
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2013/076411
Other languages
English (en)
French (fr)
Inventor
吕铭
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhejiang Sanhua Co Ltd
Original Assignee
Zhejiang Sanhua Co Ltd
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
Priority claimed from CN201210537711.3A external-priority patent/CN103868289B/zh
Priority claimed from CN201210538834.9A external-priority patent/CN103867732B/zh
Application filed by Zhejiang Sanhua Co Ltd filed Critical Zhejiang Sanhua Co Ltd
Priority to EP13862253.5A priority Critical patent/EP2933540B1/en
Priority to JP2015545637A priority patent/JP6136035B2/ja
Priority to KR1020157018084A priority patent/KR101684637B1/ko
Priority to US14/650,276 priority patent/US9890869B2/en
Publication of WO2014089953A1 publication Critical patent/WO2014089953A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F16K31/53—Mechanical actuating means with toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/54—Arrangements for modifying the way in which the rate of flow varies during the actuation of the 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
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/047—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means

Definitions

  • the invention relates to the technical field of engineering machinery, in particular to an electronic expansion valve. Background technique
  • Figure 1 is a schematic view of the structure of a typical electronic expansion valve.
  • Figure 2 is a schematic view of the structure of the valve seat and the valve stem in Figure 1.
  • the electronic inflation valve includes a valve housing 100 and a valve seat member 10.
  • the valve housing 100 and the valve seat member 10 are assembled to form a valve chamber, and the valve stem 204 is disposed in the valve chamber.
  • the valve housing 100 is provided with a motor 104 and a gear system 106.
  • the motor 104 drives the gear system 106 to rotate.
  • the gear system 106 cooperates with the valve stem 204 to drive the valve stem 204 to move up and down in the axial direction.
  • the valve seat member 10 is provided with a valve port 202, a first interface 34 and a second interface 36.
  • the opening and closing of the valve port 202 controls the communication or disconnection of the first interface 34 and the second interface 36.
  • the lower end of the valve stem 204 is the valve stem end 42.
  • the valve stem 204 is generally processed into a structure that is small and large.
  • the valve seat member 10 is of a split structure, including a valve seat base 102 and a valve seat cover 16, and the valve seat cover 16 is disposed. With an axial through hole, the valve stem 204 can move axially in the axial through hole, and the lower end of the valve seat cover 16 is crimped to the upper end of the valve seat base 102.
  • a positioning sleeve 20 is also provided, and the positioning sleeve 20 is sleeved at the crimping place of the two.
  • the valve stem 204 of the electronic expansion valve is provided with a lateral hole 205 as shown in FIG.
  • the lateral hole 204 is disposed upward, that is, the lateral hole 204 is located at the upper side of the valve stem end 42.
  • the valve port 202 is easy to open and is not easy to close.
  • the valve port 202 is easily closed and is not easy to open; when the lateral hole 202 is set downward, it is exactly the opposite. Therefore, in the expansion valve of this configuration, when the refrigerant is passed through the refrigerant in the forward and reverse directions, the valve opening resistance is not equal and it is difficult to balance.
  • the valve seat member 10 In addition, in order to realize the assembly of the valve stem 204, the valve seat member 10 needs to be designed as a split structure, and the structure is complicated. The assembled valve seat member 10 is prone to loosening due to transportation vibration or vibration of the device, resulting in refrigerant in the valve. External leakage, resulting in refrigeration failure, environmental pollution. To this end, a bowl-shaped plastic sheet 104 is provided for sealing. As shown in Fig. 1, a bowl-shaped plastic sheet 104 is disposed on the valve stem 204, and the bowl-shaped plastic sheet 104 is opened toward the valve housing 100.
  • the sealing of the bowl-shaped plastic sheet 104 can only achieve a one-way seal when the open end is high pressure (the first port 34 is in the high pressure), and if the back end is in the high pressure (the second port 36 is in the high pressure), the bowl plastic The piece 104 is forced to contract and still causes a leak.
  • the present invention provides an electronic expansion valve which is capable of balancing valve opening and valve closing capabilities.
  • the electronic expansion valve provided by the invention has a valve stem in the valve cavity, and the valve stem can axially move along the axial through hole of the valve seat of the electronic expansion valve to open or close the valve port provided on the valve seat, so as to guide Opening or disconnecting two interfaces of the electronic expansion valve, the valve stem is provided with an axial through hole communicating with the valve port, and the axial through hole sidewall of the valve seat is sealed with the valve stem;
  • the end face includes a sealing surface that is capable of sealingly contacting the end face of the valve seat at the valve port, the sealing face including a first sealing face for receiving a positive refrigerant force of an interface and for receiving another interface
  • the second sealing surface of the reverse refrigerant force, and the effective bearing areas of the first sealing surface and the second sealing surface are equal.
  • the first sealing surface of the valve stem sealing surface is only used to withstand an interface refrigerant force
  • the second sealing surface is only used to withstand the refrigerant force of the other interface
  • the first sealing surface and the second sealing surface The effective bearing area of the surface is equal, and the forced refrigerant force is balanced by the reaction force of the sealing surface at the valve port.
  • the force applied to the valve stem is only the sum of the forces applied to the first sealing surface and the second sealing surface. Assume that the inlet refrigerant pressure is P1 and the outlet refrigerant pressure is P2, which is used to withstand an interface.
  • the effective bearing area of the first sealing surface of the valve stem of the refrigerant force is S1
  • the effective sealing area of the second sealing surface of the valve stem which is subjected to the pressure of the other interface refrigerant is S2.
  • One interface acts as a refrigerant inlet
  • the other interface acts as a refrigerant outlet.
  • the valve stem is a cylindrical body, the valve stem includes a small diameter cylinder and a large diameter cylinder adjacent to the valve port; the end surface of the large diameter cylinder includes the first sealing surface and The second sealing surface.
  • the outer ring diameter of the end face of the large diameter section cylinder is greater than or equal to the outer ring diameter of the cover at the valve port; the inner ring line is smaller than the inner ring diameter of the sealing surface at the valve port;
  • D1 is the outer diameter of the small-diameter cylinder
  • D3 is the diameter of the outer ring of the valve port sealing surface
  • D4 is the inner ring diameter of the sealing surface at the valve port.
  • the outer loop diameter and the inner loop diameter of the sealing surface at the valve port satisfy the following relationship:
  • an end of the large diameter cylinder and an end of the valve seat on which the valve opening is provided are provided with chamfering.
  • the valve seat includes a valve core seat and a valve seat base body, and the two ports and the valve port are respectively disposed on the valve seat base body, and the valve core seat is inserted into the valve seat base body.
  • the axial through hole is provided in the valve core seat.
  • the valve core seat is provided with a side hole communicating with an interface, the width of the side hole is gradually increased in a direction away from the valve port, and the other interface is connected to the valve port;
  • the interface communicating with the side hole passes through the side hole and the The valve port is connected.
  • the inner side wall of the axial through hole of the valve seat and the outer side wall of the valve stem are provided with a mounting groove, and a sealing ring is disposed in the mounting groove.
  • the valve seat includes a valve core seat and a valve seat base, the valve core seat is inserted into the valve seat base body, and the axial through hole is disposed in the valve core seat;
  • the axial through hole is a stepped hole, and the stepped hole forms an annular stepped surface facing the valve housing of the electronic expansion valve; further includes a limiting sleeve, the limiting sleeve is inserted into the stepped hole, and one end of the limiting sleeve a radial boss having an annular shape, the radial boss overlapping the end surface of the valve core seat facing the valve housing; the inner side wall of the valve core seat, the limiting sleeve facing the valve port
  • the end surface, and the annular step surface form a mounting groove, and the mounting groove is provided with a sealing ring.
  • a retaining ring is disposed between the sealing ring and the annular step surface, and a small diameter side wall of the stepped hole of the valve core seat has an assembly gap with the valve stem; the retaining ring and the valve stem Clearance fit.
  • a gear system for driving axial movement of the valve stem the gear system including a limiting rod for limiting circumferential rotation of the valve stem; the limiting rod pressing the limiting sleeve to the said sleeve On the spool seat.
  • the method further includes an annular auxiliary sliding piece disposed in the mounting groove, the auxiliary sliding piece is in contact with the outer side wall of the valve stem, and the sealing ring is in the auxiliary sliding piece and the valve core seat Between the inner side walls.
  • the sliding fin has a C-shaped cross section, and the C-shaped opening faces the sealing ring.
  • the thickness of the sliding fin is between 0.2 and 0.6 mm.
  • the material of the sliding fin comprises polytetrafluoroethylene.
  • the invention also provides an electronic expansion valve, wherein a valve stem is arranged in the valve cavity, and the valve stem can be axially moved along the axial through hole of the electronic expansion valve seat to open or close the valve port provided on the valve seat
  • the valve stem is provided with an axial through hole communicating with the valve port; when the valve stem closes the valve port, it is in contact with the valve seat line;
  • the effective pressure bearing area of the upper and lower sides of the valve rod acting on the valve stem is equal, and the effective pressure bearing area of the upper and lower sides of the valve rod acting on the valve stem is equal.
  • the electronic expansion valve is in line contact with the valve seat when the valve stem closes the valve port; and, the refrigerant of one interface acts on the upper and lower effective bearing areas of the valve stem, and the refrigerant of the other interface acts on the valve stem 4
  • the effective pressure bearing area is also equal. That is, the force acting on the valve stem at the two interfaces can cancel each other out, and the force applied to the valve stem is zero regardless of the flow direction of the refrigerant, thereby equalizing the valve opening resistance of the refrigerant flow to different times, achieving equalizing the valve opening and closing the valve. The effect of ability.
  • the valve stem is a cylindrical body
  • the valve stem includes a small diameter cylinder and a large diameter cylinder adjacent to the valve port;
  • the large diameter cylinder has a breech end, and the stern end can be
  • the seat line is in contact; the diameter of the seal ring formed on the valve seat in contact with the end line is equal to the diameter of the small diameter barrel.
  • Figure 1 is a schematic view showing the structure of a typical electronic expansion valve
  • Figure 2 is a schematic view showing the structure of the valve seat and the valve stem of Figure 1;
  • FIG. 3 is a schematic structural view of a first embodiment of an electronic expansion valve according to the present invention
  • FIG. 4 is a schematic structural view of the valve rod in FIG.
  • FIG. 5 is a schematic structural view of the valve stem of Figure 3.
  • Figure 6 is a partial enlarged view of the portion B of Figure 3;
  • FIG. 7 is a schematic structural view of a second embodiment of an electronic expansion valve according to the present invention
  • FIG. 8 is a partially enlarged schematic view showing a portion C of FIG. 7;
  • Figure 9 is a schematic structural view of the spool seat of Figure 1;
  • Figure 10 is a schematic view showing the assembly of the valve stem and the limit sleeve of Figure 3;
  • Figure 11 is a schematic structural view of the components of Figure 10 after assembly
  • Figure 12 is a partial enlarged view of the portion A of Figure 3;
  • Figure 13 is a schematic structural view of the gear system of Figure 3;
  • Figure 14 is a schematic structural view of the valve stem of Figure 3.
  • Figure 15 is a schematic view showing the structure of the gear system and the valve stem of Figure 3;
  • valve housing 100 valve housing, 104 motor, 106 gear system, 10 seat part, 204 stem, 42 stem ⁇ , 205 lateral hole, 34 first interface, 36 second interface, 202 valve port, 16 valve seat cover, 20 positioning sleeve, 102 valve seat base, 104 bowl plastic piece;
  • Figure 3-15
  • valve housing 22 motor, 23 gear system, 231 gear, 232 limit rod, 233 screw,
  • FIG. 3 is a schematic structural view of a first embodiment of an electronic expansion valve according to the present invention.
  • FIG. 4 is a schematic structural view of the valve rod in FIG.
  • the electronic expansion valve is provided with a valve rod 24 in the valve chamber, and the valve rod 24 can be axially moved along the axial through hole of the electronic expansion valve seat to open or close the valve port 251 provided on the valve seat, so as to guide
  • the two ports of the electronic expansion valve are opened or closed, and the first port tube 31 and the second port tube 32, which are respectively connected to the first port and the second port, are shown in Figs.
  • valve stem 24 is provided with an axial through hole communicating with the valve port 251.
  • the valve port 251 and the second interface are always electrically connected, and the second interface and the valve stem 24 are The axial through holes communicate, and the refrigerant in the second port 32 can enter the upper cavity (a portion of the valve cavity) of the valve stem 24 through the axial through hole of the valve stem 24.
  • the axial through-hole side wall of the valve seat needs to be sealed with the valve stem 24, and the seal described here does not define that the entire side wall of the axial through-hole of the valve seat is sealed with the valve stem 24, in fact, part
  • the contact sealing is also possible, as long as the upper cavity of the valve stem 24 and the first interface are not communicated through the gap between the valve stem 24 and the sidewall of the axial through hole of the valve seat, so as to ensure that only the valve port 251 is opened after the two interfaces are opened. To be connected.
  • the end surface of the valve stem 24 can be in contact with the end surface of the valve seat at the valve opening 251, and the end faces that are in contact with each other are respective sealing faces.
  • 3 shows the valve port 251 in an open state, and the valve stem 24 is moved downward to seal the sealing surface of the valve stem 24 with the sealing surface of the valve port 251, the valve port 251 shut down.
  • the sealing surface of the valve stem 24 includes a first sealing surface and a second sealing surface.
  • the first sealing surface is only used to withstand an interface refrigerant force
  • the second sealing surface is only used to withstand the refrigerant force of the other interface.
  • the refrigerant force that is subjected to the load is balanced by the reaction force of the sealing surface at the valve port 251.
  • the effective bearing area of the first sealing surface and the second sealing surface are equal, and the effective bearing area is the projected area on the surface perpendicular to the pressure direction of the refrigerant.
  • the downward force of the refrigerant is balanced by the upward force, that is, the force applied to the valve stem 24 is only the first sealing surface and the second sealing surface. The sum of the forces received.
  • the effective sealing area of the first sealing surface of the valve stem 24 for receiving the pressure of one interface refrigerant is S1, and the valve stem 24 of the other interface is subjected to the refrigerant force of the other interface.
  • the effective bearing area of the second sealing surface is S2.
  • the electronic expansion valve of the structure has the same valve opening resistance as the valve body 24, and accordingly, the valve closing resistance is equal, thereby equalizing the valve opening and closing ability.
  • the valve stem 24 is subjected to downward refrigerant resistance regardless of the flow direction of the refrigerant, thereby improving the sealing property of the valve opening 251, and helping to cut off the communication between the first interface and the second interface. Make sure you don't leak.
  • the size of S1 ie S2 can be reasonably designed to strike a balance between valve opening resistance and valve closing assistance.
  • the effective bearing areas of the first sealing surface and the second sealing surface should be equal to each other, and a slight deviation can also achieve the balance purpose; and based on the machining error, it is actually difficult to ensure that the effective bearing area is completely equal.
  • valve stem 24 may be a cylindrical body, and the valve stem 24 includes a small diameter cylinder 24a and a large diameter cylinder 24b close to the valve opening 251.
  • the small diameter cylinder 24a is sealed with the valve seat;
  • the end surface of the body 24b can be in contact with the end surface of the valve port 251, as shown in Fig. 5.
  • Fig. 5 is a schematic structural view of the valve stem of Fig. 3.
  • FIG. 6 is a partial enlarged view of the portion B of FIG. 3, and FIG. 6 shows The valve port 251 is in a closed state.
  • the refrigerant enters from the first interface, the pressure is P1, the pressure at the second interface is P2, and when the flow direction is opposite, the pressure is exactly opposite to that of Fig. 6.
  • the entire end surface at the valve port 251 is a sealing surface.
  • the first sealing surface area S1 X ( D3 2 - Dl 2 ) /4 for withstanding the first interface refrigerant force.
  • the end face of the valve stem 24 in contact with the sealing surface of the valve port 251 is bounded by a broken line, and the first sealing surface on the left side of the broken line is subjected to the first interface refrigerant force (the refrigerant acts on the large diameter cylinder)
  • the force of the step surface formed by the 24b and the small diameter section cylinder 24a is transmitted to the first sealing surface
  • the second sealing surface of the right side of the broken line is subjected to the second interface refrigerant force (the refrigerant in the upper cavity of the valve stem 24 acts on the valve stem 24) Part of the force)
  • the refrigerant force on the non-sealing surface of the valve stem 24 end face cancels each other up and down.
  • outer ring diameter and the inner ring diameter of the sealing surface at the valve port 251 can satisfy the following relationship:
  • the end face at the valve port 251 i.e., the sealing face, that is, the end face of the valve stem 24 can cover the end face.
  • the optimum range of the difference between the inner ring diameter D4 and the outer ring diameter D3 of the sealing surface at the valve port 251 is: 0.4 mm ⁇ D4-D3 ⁇ 3 mm, so that the valve stem 24 is sufficiently small in resistance. , can guarantee that no leakage.
  • the end surface of the valve stem 24 is a plane perpendicular to the direction of the pressure of the refrigerant, and the area of the first sealing surface and the second sealing surface is the effective bearing area, so the first sealing surface and the second sealing surface area When it is equal, it can guarantee that the effective bearing area of the two is equal.
  • the first sealing surface and the second sealing surface are not limited to the plane in FIG. 6, and the end surface of the valve stem 24 is a sloped surface so that the inclination angles of the first sealing surface and the second sealing surface are the same.
  • valve stem structure can also be used in a split type to facilitate processing and improve design accuracy.
  • FIG. 7 is a schematic structural view of a second embodiment of the electronic expansion valve according to the present invention.
  • FIG. 8 is a partially enlarged schematic view of the C portion of FIG.
  • valve cavity 24 is provided in the valve cavity of the electronic inflation valve, and the valve stem 24 is also provided with an axial through hole communicating with the valve port 251, so that the valve stem 24 is subjected to the force of the upper cavity refrigerant.
  • the valve stem 24 closes the valve port 251, it is in line contact with the valve seat; and, the refrigerant of one interface acts on the upper and lower effective bearing areas of the valve stem 24, and the refrigerant of the other interface acts on the upper and lower sides of the valve stem 24.
  • the effective bearing area is equal.
  • the effective bearing area is the projected area on the surface perpendicular to the direction of the refrigerant pressure.
  • the forces acting on the valve stem 24 at the first interface and the second interface can cancel each other out, and regardless of the flow direction of the refrigerant, the force applied to the valve stem 24 is zero, thereby equalizing the valve opening resistance of the refrigerant flow to different times.
  • the valve stem 24 may also be a cylindrical body, and specifically includes a small diameter section cylinder 24a and a large diameter section cylinder 24b near the valve opening 251;
  • the end portion of the large-diameter cylinder 24b and the one end of the valve seat 251 provided on the valve seat are provided with chamfers. As shown in Figures 6 and 8, the design has a good steady flow effect on the refrigerant.
  • the contact between the valve seat and the end of the valve seat is an ideal state, and in the actual use structure, there may be a small surface contact, causing the interface to act on the valve stem. There may be slight deviations in the effective bearing area; and, based on machining errors, such subtle deviations are actually difficult to avoid. It should be understood that as long as the two interfaces act on the top and bottom of the valve stem The effective bearing areas are approximately equal, and the effect of equalizing the valve opening and closing ability can be achieved, and should be within the scope of the present invention.
  • the valve seat may specifically include a valve core seat 26 and a valve seat base body 25, and the two interfaces (ie, the first interface, the second interface) and the valve port 251 are both formed on the valve seat base 25, and the valve core seat 26 Inserted into the valve seat base 25, the axial through hole is provided in the spool seat 26, as shown in FIG.
  • the valve seat is provided as a separate structure of the valve seat base 25 and the valve core seat 26 to facilitate the installation of the valve stem 24, especially when the valve stem 24 is machined to have a stepped upper and lower large structure.
  • FIG. 9 is a schematic structural view of the spool seat of FIG.
  • the side holes 262 communicate with the first interface, and the width of the side holes 262 gradually increases in a direction away from the valve port 251.
  • the first port can communicate with the valve port 251 through the side hole 262; and as the valve stem 24 is gradually moved upward, the area of the side hole 262 through which the refrigerant flows is gradually increased. Thereby, the effect of adjusting the flow rate of the refrigerant through the axial movement of the valve stem 24 is achieved.
  • the inner side wall of the axial through hole of the valve seat and the outer side wall of the valve stem 24 may be provided with a mounting groove, and a sealing ring 271 is disposed in the mounting groove.
  • the sealing ring 271 provides a good sealing performance between the valve seat and the valve stem 24, and the sealing ring 271 in this embodiment can achieve a two-way sealing regardless of the manner of sealing by the bowl-shaped plastic sheet in the background art, regardless of the refrigerant The flow direction can maintain a good sealing effect.
  • valve seat comprises a valve core seat 26 and a valve seat base body 25
  • the valve port 251 is opened on the valve seat base body 25
  • the valve core seat 26 is inserted into the valve seat base body 25
  • the axial through hole is provided in the valve core seat 26, such as As shown in Fig. 4, the axial through hole of the spool seat 26 can be provided as a stepped hole which forms an annular stepped surface 261 facing the valve casing 21.
  • the electronic expansion valve may further include a limiting sleeve 29, and the limiting sleeve 29 is inserted into the stepped hole. As shown in FIG. 3, one end portion of the limiting sleeve 29 has an annular radial boss.
  • the specific structure of the limiting sleeve 29 can be referred to the drawing. 10-11 understanding, FIG. 10 is a schematic view showing the assembly of the valve stem and the limiting sleeve of FIG. 3; FIG. 11 is a schematic structural view of the components of FIG.
  • Fig. 12 is a partially enlarged schematic view of the portion A of Fig. 3.
  • valve stem 24 can be assembled into the valve core seat 26 first, and then the sealing ring 271 and the limiting sleeve 29 are sequentially loaded; or, as shown in FIG. 11, the sealing ring 271 is limited. After the sleeve 29 and the valve stem 24 are engaged, the spool seat 26 is integrally inserted. Of course, it is also possible to provide the mounting groove on the valve stem 24. In view of the strength and design requirements of the valve stem 24, it is preferred to provide it on the valve seat.
  • a retaining ring 28 may be disposed between the sealing ring 271 and the annular stepped surface 261.
  • the inner side wall of the small diameter hole of the valve core seat 26 and the valve stem 24 have a certain fitting gap ⁇ .
  • the assembly clearance ⁇ is larger than the diameter difference between the two portions, thereby facilitating assembly; the retaining ring 28 and the valve stem 24 can be fitted with a small gap, and at this time, the arrangement of the retaining ring 28 can be prevented. Due to the assembly gap ⁇ , the seal ring 271 is disengaged from the mounting groove during the reciprocating motion of the valve stem 24.
  • the assembled limit sleeve 29 and the spool seat 26 need to be relatively fixed, and can be fixed by welding, screwing, etc. after assembly.
  • the electronic expansion valve in this embodiment can achieve the fixing of the limit sleeve 29 and the spool seat 26 through the gear system 23.
  • FIG. 13 is a schematic structural view of the gear system of FIG. 3;
  • FIG. 14 is a schematic structural view of the valve stem of FIG. 3; and
  • FIG. 15 is a structural schematic view of the gear system and the valve stem of FIG.
  • the electronic expansion valve may include a gear system 23 that drives the valve rod 24 to move axially.
  • the gear system 23 includes a gear 231 and a screw 233.
  • the motor 22 of the electronic expansion valve drives the gear 231 of the gear system 23 to rotate.
  • the gear 231 rotates
  • the screw 233 is rotated, and the screw 233 is threadedly engaged with the valve stem 24.
  • the gear system 23 may further include a limiting rod 232 for restricting the circumferential rotation of the valve stem 24. As shown in FIG.
  • the upper end of the valve stem 24 is provided with a buckle 241, and the buckle 241 is provided.
  • the boss 241a is caught between the two limit bars 232. Since the position of the limit bar 232 is fixed, the buckle 241 cannot rotate, thereby restricting the circumferential rotation of the valve stem 24, and only the axial movement is possible.
  • the limit lever 232 of the gear system 23 can press the limit sleeve 29 against the upper end surface of the spool seat 26, as shown in FIG.
  • the structure uses the limiting rod 232 of the gear system 23 to press the limiting sleeve 29 to fix the limiting sleeve 29 and the valve core seat 26, has a simple structure, and is easy to assemble and disassemble, so that the limiting sleeve 29 and the sealing ring
  • the replacement of components such as 271 is very simple.
  • the electronic expansion valve further includes an annular auxiliary sliding piece 272 disposed in the mounting groove.
  • the auxiliary sliding piece 272 is in contact with the outer side wall of the valve stem 24, and the sealing ring 271 is in the auxiliary sliding piece 272 and the valve. Between the inner side walls of the core seat 26.
  • the slide 272 is set to have both sealing and sliding properties.
  • the cross section of the sliding fin 272 may be C-shaped, and the C-shaped opening faces the sealing ring 271.
  • the curvature of the C-shaped auxiliary sliding piece 272 facilitates the assembly guiding of the valve stem 24, because the surface of the C-shaped auxiliary sliding piece 272 and the sealing ring 271 Cooperate to avoid relative slippage of the slide 272 and the seal ring 271 during assembly.
  • the design is such that the assisting slide 272 easily senses the amount of deformation of the seal ring 271; in addition, the contact area of the slide vane 272 with the valve stem 24 is relatively small, further reducing the frictional resistance of the valve stem 24 when it moves axially.
  • the thickness of the sliding fin 272 may be between 0.2 and 0.6 mm, and the thickness of the sliding fin 272 can more sensitively sense the amount of deformation of the sealing ring 271 so as to be in close contact with the stem 24 to ensure sealing.
  • the material of the sliding fin 272 may contain polytetrafluoroethylene (PTFE).
  • PTFE polytetrafluoroethylene
  • the sliding fin 272 is also made of a general plastic material.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lift Valve (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Details Of Valves (AREA)

Abstract

提供了一种电子膨胀阀，其阀腔中设有阀杆（24），阀杆（24）能够沿电子膨胀阀阀座的轴向通孔轴向移动以开启或关闭设于阀座上的阀口（251）。阀杆（24）设有连通阀口（251）的轴向通孔，阀座的轴向通孔侧壁与阀杆（24）密封。阀杆（24）的端面包括与阀座上位于阀口（251）处的端面接触密封的密封面，密封面包括用于承受一接口冷媒作用力的第一密封面和承受另一接口冷媒作用力的第二密封面，且第一密封面和第二密封面的有效承压面积相等。阀杆（24）所受的作用力仅为第一密封面和第二密封面所受的作用力之和，由于两个有效承压面积相等，则无论冷媒从哪个接口进入，阀杆（24）受力相等，从而均衡了开阀和闭阀能力。也提供了一种与阀座线接触密封的电子膨胀阀，且一接口的冷媒作用于阀杆（24）的上、下有效承压面积相等，另一接口的冷媒作用于阀杆的上、下有效承压面积相等。

Description

电子膨胀阀
本申请要求于 2012 年 12 月 11 日提交中国专利局、 申请号为 201210537711.3、 发明名称为"电子膨胀阀"， 以及同日申请的申请号为 201210538834.9、 发明名称为 "电子膨胀阀" 的中国专利申请的优先权， 其全部内容通过引用结合在本申请中。 技术领域
本发明涉及工程机械技术领域， 特别涉及一种电子膨胀阀。 背景技术
请参考图 1-2, 图 1为一种典型的电子膨胀阀的结构示意图； 图 2为 图 1中阀座和阀杆配合的结构示意图。
电子膨月长阀包括阀壳 100、 阀座部件 10, 阀壳 100和阀座部件 10安装 后形成阀腔， 阀杆 204设置于阀腔内。 阀壳 100内设有电机 104和齿轮系 统 106 , 电机 104驱动齿轮系统 106转动， 齿轮系统 106与阀杆 204配合， 以驱动阀杆 204沿轴向上下移动。
阀座部件 10上开设有阀口 202、第一接口 34和第二接口 36,阀口 202 的开启和关闭控制第一接口 34、 第二接口 36的连通或断开。 如图 1所示， 阀杆 204的下端为阀杆雉端 42 , 阀杆 204下移而封堵阀口 202时， 第一接 口 34和第二接口 36断开； 阀杆 204上移而离开阀口 202时， 第一接口 34 和第二接口 36连通。
阀杆 204—般加工为上小下大的结构， 为了保证该结构的阀杆 204能 够装配， 阀座部件 10为分体式结构， 包括阀座基体 102和阀座套 16, 阀 座套 16设置有轴向通孔， 阀杆 204能够在轴向通孔内轴向移动， 阀座套 16的下端压接在阀座基体 102的上端，为了保证阀座套 16和阀座基体 102 可靠连接， 还设置定位套 20, 定位套 20外套于二者的压接处。
为了提高阀的性能， 电子膨胀阀的阀杆 204上开设有侧向孔 205 , 如 图 2所示。 当侧向孔 204偏上设置时， 即侧向孔 204位于阀杆雉端 42的上 侧， 此时， 若自第二接口 36进高压， 则阀口 202易于打开， 不易于关闭， 若自第一接口 34进高压， 则阀口 202易于关闭， 不易于打开； 当侧向孔 202偏下设置时， 与上述情况恰好相反。 因此， 该结构的膨胀阀， 正反向 通冷媒时， 开阀阻力不等， 难以均衡。
此外， 为了实现阀杆 204的装配， 阀座部件 10需设计为分体式结构， 结构复杂，组装的阀座部件 10因为运输振动或受到设备振动的影响，容易 发生松动， 导致阀内的制冷剂外漏， 造成制冷失效， 环境污染。 为此， 设 置了碗状塑料片 104用于密封， 如图 1所示， 碗状塑料片 104设置于阀杆 204上， 碗状塑料片 104开口朝向阀壳 100方向。
然而， 碗状塑料片 104 的密封只能实现开口端为高压 （第一接口 34 进高压） 时的单向密封， 若背向开口端进高压 （第二接口 36进高压）， 则 碗状塑料片 104受力收缩， 仍然造成泄漏。
有鉴于此， 如何改进电子膨胀阀结构， 以均衡开阀、 闭阀能力， 是本 领域技术人员亟待解决的技术问题。
发明内容
为解决上述技术问题， 本发明提供一种电子膨胀阀， 该电子膨胀阀能 够均衡开阀、 闭阀能力。
本发明提供的电子膨胀阀， 其阀腔中设有阀杆， 阀杆能够沿电子膨胀 阀阀座的轴向通孔作轴向移动以开启或关闭设于阀座上的阀口， 以便导通 或断开电子膨长阀的两个接口， 所述阀杆设有连通阀口的轴向通孔， 所述 阀座的轴向通孔侧壁与所述阀杆密封； 所述阀杆的端面包括能够与阀座上 位于所述阀口处的端面接触密封的密封面， 所述密封面包括用于承受一接 口的正向冷媒作用力的第一密封面和用于承受另一接口的反向冷媒作用力 的第二密封面，且所述第一密封面和所述第二密封面的有效承压面积相等。
该电子膨胀阀中， 阀杆密封面的第一密封面仅用于承受一接口冷媒作 用力， 第二密封面仅用于承受另一接口的冷媒作用力， 且第一密封面和第 二密封面的有效承压面积相等， 承受的冷媒作用力均由阀口处密封面的反 作用力平衡。 阀杆所受的作用力仅为第一密封面和第二密封面所受的作用 力之和。 假设进口冷媒压力为 P1 , 出口冷媒压力为 P2, 用于承受一接口 冷媒作用力的阀杆第一密封面有效承压面积为 S1 ,承受另一接口冷媒作用 力的阀杆第二密封面有效承压面积为 S2。 一接口作为冷媒进口， 另一接口 作为冷媒出口时， 阀杆受力 F1=P1S1+P2S2; 另一接口作为冷媒进口， 一 接口作为冷媒出口时， 阀杆受力 F2=P1 S2+P2S1。 由于 S1=S2, 则 F1=F2, 因此， 同一压力的冷媒自任一接口进入时， 阀杆受力均相等， 且始终受到 向下的力。 可见， 该结构的电子膨胀阀， 无论冷媒流动方向如何， 阀杆受 到的开阀阻力相等， 相应地， 闭阀阻力也相等， 从而均衡了开阀和闭阀能 力。 另外， 阀杆关闭时， 无论冷媒流动方向如何， 阀杆均受到向下的冷媒 阻力， 从而提高阀口的密封性， 有助于切断两接口的连通， 确保不泄漏。
优选地， 所述阀杆为圓筒状体， 所述阀杆包括小径段筒体和靠近阀口 的大径段筒体； 所述大径段筒体的端面包括所述第一密封面和所述第二密 封面。
优选地， 所述大径段筒体端面的外环线直径大于或等于所述阀口处密 封面的外环线直径； 内环线小于所述阀口处密封面的内环线直径；
且满足下述关系式：
Dl~ ( D3+D4 ) /2;
其中， D1为小径段筒体的外径、 D3为阀口密封面的外环线直径、 D4 为阀口处密封面的内环线直径。
优选地， 所述阀口处密封面的外环线直径和内环线直径满足下述关系 式：
0.4mm<D3 -D4<4mm。
优选地， 所述大径段筒体的端部和所述阀座上设置所述阀口的一端均 设置有倒角。
优选地， 所述阀座包括阀芯座和阀座基体， 两所述接口和所述阀口均 开设于所述阀座基体上， 所述阀芯座插装于所述阀座基体内， 所述轴向通 孔设于所述阀芯座。
优选地， 所述阀芯座开设有与一所述接口连通的侧孔， 所述侧孔的宽 度沿背离所述阀口的方向渐增， 另一所述接口与所述阀口连通； 所述阀杆 沿轴向移动脱离阀口时， 与所述侧孔连通的所述接口通过所述侧孔与所述 阀口连通。
优选地， 所述阀座轴向通孔的内侧壁和所述阀杆的外侧壁， 二者之一 设有安装槽， 所述安装槽内设有密封圈。
优选地， 所述阀座包括阀芯座和阀座基体， 所述阀芯座插装于所述阀 座基体内， 所述轴向通孔设于所述阀芯座； 所述阀芯座的所述轴向通孔为 台阶孔， 台阶孔形成朝向电子膨胀阀阀壳的环形台阶面； 还包括限位套， 所述限位套插入所述台阶孔， 所述限位套的一端部具有环形的径向凸台， 所述径向凸台搭接于所述阀芯座朝向所述阀壳的端面；所述阀芯座内侧壁、 所述限位套上朝向所述阀口的端面， 以及所述环形台阶面形成安装槽， 所 述安装槽内设有密封圈。
优选地， 所述密封圈和所述环形台阶面之间设有挡圈， 所述阀芯座台 阶孔的小径段侧壁与所述阀杆具有装配间隙； 所述挡圈与所述阀杆间隙配 合。
优选地， 还包括驱动所述阀杆轴向移动的齿轮系统， 所述齿轮系统包 括限制所述阀杆周向转动的限位杆； 所述限位杆压紧所述限位套于所述阀 芯座上。
优选地， 还包括设于所述安装槽内的呈环形的助滑片， 所述助滑片与 所述阀杆外侧壁接触， 所述密封圈处于所述助滑片和所述阀芯座的内侧壁 之间。
优选地， 所述助滑片的截面呈 C形， 且 C形开口朝向所述密封圈。 优选地， 所述助滑片的厚度处于 0.2〜0.6mm之间。
优选地， 所述助滑片的材料包括聚四氟乙烯。 本发明还提供一种电子膨胀阀， 其阀腔中设有阀杆， 阀杆能够沿电子 膨长阀阀座的轴向通孔作轴向移动以开启或关闭设于阀座上的阀口， 以便 导通或断开电子膨胀阀的两个接口， 所述阀杆设有连通阀口的轴向通孔； 所述阀杆关闭所述阀口时， 与所述阀座线接触； 一所述接口的冷媒作用于 所述阀杆的上、 下有效承压面积相等， 另一所述接口的冷媒作用于所述阀 杆的上、 下有效承压面积相等。 该电子膨胀阀在阀杆关闭阀口时， 与阀座线接触； 且， 一接口的冷媒 作用于阀杆的上、 下有效承压面积相等， 另一接口的冷媒作用于阀杆 4的 上、 下有效承压面积也相等。 即两接口处冷媒作用于阀杆的作用力可以相 互抵消， 则无论冷媒流向如何， 阀杆受到的作用力均为零， 从而均衡冷媒 流向不同时的开阀阻力， 达到均衡开阀、 闭阀能力的效果。
优选地， 所述阀杆为圓筒状体， 所述阀杆包括小径段筒体和靠近阀口 的大径段筒体； 大径段筒体具有雉端， 所述雉端能够与所述阀座线接触； 所述阀座上与所述雉端线接触时形成的密封环线的直径与小径段筒体直径 相等。 附图说明
图 1为一种典型的电子膨胀阀的结构示意图；
图 2为图 1中阀座和阀杆配合的结构示意图；
图 3为本发明所提供电子膨胀阀第一种具体实施方式的结构示意图； 图 4为图 3中未设置阀杆时的结构示意图；
图 5为图 3中阀杆的结构示意图；
图 6为图 3中 B部位的局部放大示意图；
图 7为本发明所提供电子膨胀阀第二种具体实施方式的结构示意图； 图 8为图 7中 C部位的局部放大示意图；
图 9为图 1中阀芯座的结构示意图；
图 10为图 3中阀杆与限位套的装配示意图；
图 11为图 10中各部件装配后的结构示意图；
图 12为图 3中 A部位的局部放大示意图；
图 13为图 3中齿轮系统的结构示意图；
图 14为图 3中阀杆的结构示意图；
图 15为图 3中齿轮系统和阀杆配合的结构示意图。 图 1-2中：
100阀壳、 104电机、 106齿轮系统、 10阀座部件、 204阀杆、 42阀杆 雉端、 205侧向孔、 34第一接口、 36第二接口、 202阀口、 16阀座套、 20 定位套、 102阀座基体、 104碗状塑料片； 图 3-15中：
21阀壳、 22电机、 23齿轮系统、 231齿轮、 232限位杆、 233丝杆、
24阀杆、 24b大径段筒体、 24a小径段筒体、 241卡扣、 241a凸台、 25阀 座基体、 251阀口、 26阀芯座、 261环形台阶面、 262侧孔、 271密封圈、 272助滑片、 28挡圈、 29限位套、 31第一接口管、 32第二接口管 具体实施方式
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 3-4, 图 3为本发明所提供电子膨胀阀第一种具体实施方式 的结构示意图； 图 4为图 3中未设置阀杆时的结构示意图。
该电子膨胀阀， 其阀腔中设有阀杆 24 , 阀杆 24能够沿电子膨胀阀阀 座的轴向通孔作轴向移动以开启或关闭设于阀座上的阀口 251 , 以便导通 或断开电子膨胀阀的两个接口， 图 3、 4中示出分别与第一接口和第二接口 连接的第一接口管 31和第二接口管 32。
另外， 该实施例中， 阀杆 24设有连通阀口 251 的轴向通孔， 从图 3 中可以看出， 阀口 251与第二接口始终导通， 则第二接口与阀杆 24的轴向 通孔连通， 第二接口管 32内的冷媒可以通过阀杆 24的轴向通孔进入阀杆 24的上部腔体（阀腔的一部分） 中。 为了保证密封， 显然， 阀座的轴向通 孔侧壁需与阀杆 24密封，此处所述的密封并非限定阀座轴向通孔的整个侧 壁与阀杆 24密封， 实际上， 部分接触密封也是可以的， 只要保证阀杆 24 上部腔体与第一接口不会通过阀杆 24 和阀座轴向通孔侧壁之间空隙连通 即可， 以保证两接口只有阀口 251开启后才能连通。
阀杆 24的端面能够与阀座上位于阀口 251处的端面接触密封，二者接 触的端面部分为各自的密封面。 图 3所示为阀口 251处于开启状态， 阀杆 24下移而使阀杆 24的密封面与阀口 251处密封面密封贴合时， 阀口 251 关闭。
本实施例中， 阀杆 24密封面包括第一密封面和第二密封面，第一密封 面仅用于承受一接口冷媒作用力， 第二密封面仅用于承受另一接口的冷媒 作用力， 承受的冷媒作用力均由阀口 251处密封面的反作用力平衡。 且第 一密封面和第二密封面的有效承压面积相等， 有效承压面积为在与冷媒压 力方向垂直的面上的投影面积。 阀杆 24密封面小于阀杆 24端面面积时， 冷媒向下的部分作用力由向上的作用力平衡 4氏消，即阀杆 24所受的作用力 仅为第一密封面和第二密封面所受的作用力之和。
4叚设进口冷媒压力为 P1 , 出口冷媒压力为 P2, 用于承受一接口冷媒 作用力的阀杆 24第一密封面有效承压面积为 S1 , 承受另一接口冷媒作用 力的阀杆 24第二密封面有效承压面积为 S2。 第一接口作为冷媒进口， 第 二接口作为冷媒出口时， 阀杆 24受力 F1=P1S1+P2S2; 第二接口作为冷媒 进口，第一接口作为冷媒出口时，阀杆 24受力 F2=P1S2+P2S1。由于 S1=S2, 贝' J F1=F2, 因此， 同一压力的冷媒自任一接口进入时，阀杆 24受力均相等， 按照图 3的视角， 阀杆 24始终受到向下的力。
可见， 该结构的电子膨胀阀， 无论冷媒流动方向如何， 阀杆 24受到的 开阀阻力相等， 相应地， 闭阀阻力也相等， 从而均衡了开阀和闭阀能力。 另夕卜， 阀杆 24关闭时 , 无论冷媒流动方向如何， 阀杆 24均受到向下的冷 媒阻力， 从而提高阀口 251的密封性， 有助于切断第一接口和第二接口的 连通， 确保不泄漏。 当然， 可以合理设计 S1 (即 S2 ) 的大小， 以在开阀 阻力和闭阀助力之间取得平衡。
可以理解， 第一密封面和第二密封面的有效承压面积相等应当是大致 相等的状态， 略有偏差也是可以达到平衡目的的； 而且基于加工误差， 实 际上也难以保证有效承压面积完全相等。
具体地， 阀杆 24可以为圓筒状体， 阀杆 24包括小径段筒体 24a和靠 近阀口 251的大径段筒体 24b, 小径段筒体 24a与阀座保持密封； 大径段 筒体 24b的端面能够与阀口 251处的端面接触密封， 如图 5所示， 图 5为 图 3中阀杆的结构示意图。
请继续参考图 6, 图 6为图 3中 B部位的局部放大示意图， 图 6显示 阀口 251处于关闭状态。 图 6中， 冷媒自第一接口进入， 压力为 P1 , 第二 接口处的压力为 P2, 流向相反时， 压力与图 6恰好相反。
当大径段筒体 24b端面的外环线直径 D2大于或等于阀口 251处密封 面的外环线直径 D3 , 且内环线直径小于阀口 251 处密封面的内环线直径 D4时；
可以满足下述关系式：
Dl~ ( D3+D4 ) /2;
此时， 阀口 251处的整个端面均为密封面。 用于承受第一接口冷媒作 用力的第一密封面面积 S1 = X ( D32-Dl2 ) /4。 用于承受第二接口冷媒作 用力的第二密封面面积 Ξ2 = πχ ( Dl2- D42 ) /4, Dl= ( D3+D4 ) 12时， S1 恰好与 S2相等， 如上所述 S1 S2也是可以满足平衡需求的； 而且由于加 工误差， 也允许 S 1和 S2存在细微的偏差。 从图 6中可以看出， 阀杆 24 与阀口 251处密封面接触的端面以虚线为界， 虚线左侧的第一密封面承受 第一接口冷媒作用力 (冷媒作用于大径段筒体 24b和小径段筒体 24a形成 的台阶面的力传递至第一密封面），虚线右侧的第二密封面承受第二接口冷 媒作用力 （阀杆 24上部腔体中冷媒作用于阀杆 24的部分力）， 阀杆 24端 面的非密封面所受的冷媒作用力上下相互抵消。 该种设计方式简单地实现 了承受不同接口冷媒作用力的密封面面积相等。
进一步地， 阀口 251处密封面的外环线直径和内环线直径可以满足下 述关系式：
0.4mm<D3 -D4<4mm。
该实施例中， 阀口 251处的端面即密封面， 即阀杆 24的端面可以覆盖 住该端面。 此时， D3、 D4数值越接近， 阀口 251处密封面的环形面积越 小， 阀杆 24受到的向下冷媒作用力越小， 轴向运行受到阻力就越小， 根据 密封面受力应变强度与密封效果综合考虑， 阀口 251处密封面的内环线直 径 D4与外环线直径 D3差值的最佳范围为： 0.4mm≤D4-D3≤3mm, 如此设 计， 阀杆 24受到阻力足够小， 又能保证不泄漏。
图 6中， 阀杆 24的端面为与冷媒压力方向垂直的平面， 则第一密封面 和第二密封面的面积即有效承压面积， 故第一密封面和第二密封面面积相 等时， 即可保证二者的有效承压面积相等。 当然， 第一密封面和第二密封 面并非限定于图 6中的平面， 阀杆 24的端面为斜面， 以使第一密封面和第 二密封面的倾斜角度相同也是可以的。
针对上述各实施例， 阀杆结构也可以釆用分体式， 以便于加工和提高 设计精度。
除了上述方式， 还可以通过其他方式实现冷媒流向不同时， 开阀阻力 的均衡。 如图 7和图 8所示， 图 7为本发明所提供电子膨胀阀第二种具体 实施方式的结构示意图； 图 8为图 7中 C部位的局部放大示意图。
该实施例中， 电子膨月长阀的阀腔中设有阀杆 24 , 阀杆 24也设有连通 阀口 251的轴向通孔， 则阀杆 24会受到上部腔体冷媒的作用力。 阀杆 24 关闭阀口 251时， 与阀座线接触； 且 , 一接口的冷媒作用于阀杆 24的上、 下有效承压面积相等， 另一接口的冷媒作用于阀杆 24的上、下有效承压面 积相等， 同样，有效承压面积为在与冷媒压力方向垂直的面上的投影面积。 即第一接口和第二接口处冷媒作用于阀杆 24的作用力可以相互抵消，则无 论冷媒流向如何， 阀杆 24受到的作用力均为零，从而均衡冷媒流向不同时 的开阀阻力。
该实施例中， 与上述圓筒体阀杆 24的实施例类似， 阀杆 24也可以为 圓筒状体， 并具体包括小径段筒体 24a和靠近阀口 251的大径段筒体 24b; 此外， 该实施例中的大径段筒体 24b具有雉端， 雉端能够与阀座线接触密 封； 阀座上与雉端线接触时形成的密封环线的直径与小径段筒体 24a直径 相等， 即 D1=D5 , 其中， D1为小径段筒体 24a外环线直径， D5为密封环 线的直径， 可见， 虚线左侧的上、 下有效承压面积相等， 虚线右侧的上、 下有效承压面积也相等。
针对上述实施例， 大径段筒体 24b的端部和阀座上设置阀口 251的一 端均设置有倒角。如图 6、 8所示，该设计对冷媒能够起到良好的稳流作用。
需要提出的是，在本实施例中， "阀座上与雉端线接触"是为理想状态， 在实际使用的结构中， 可能会有较小的面接触， 导致接口作用于阀杆上的 上、 下有效承压面积可能出现细微的偏差； 而且， 基于加工误差， 该种细 微偏差实际上也难以避免。 应当理解， 只要是两接口作用于阀杆的上、 下 有效承压面积均大致相等， 就可以达到均衡开阀和闭阀能力的效果， 都应 该在本发明的保护范围中。
上述各实施例中 , 阀座具体可以包括阀芯座 26和阀座基体 25 , 两接 口 （即第一接口、 第二接口）和阀口 251均开设于阀座基体 25上， 阀芯座 26插装于阀座基体 25内， 轴向通孔设于阀芯座 26, 如图 4所示。 阀座设 置为阀座基体 25和阀芯座 26的分体式结构，有助于阀杆 24的安装，尤其 当阀杆 24加工为具有台阶的上小下大结构时， 该优势更为明显。
具体地， 阀芯座 26可以开设与一接口连通的侧孔 262, 如图 9所示 , 图 9为图 3中阀芯座的结构示意图。
从图 3、 4可以看出， 侧孔 262与第一接口连通， 侧孔 262的宽度沿背 离阀口 251的方向渐增。则阀杆 24沿轴向移动脱离阀口 251时，第一接口 可以通过侧孔 262与阀口 251连通； 且随着阀杆 24的逐渐上移，供冷媒流 通的侧孔 262面积渐增，从而达到通过阀杆 24轴向移动调节冷媒流量的作 用。
针对上述各实施例， 阀座轴向通孔的内侧壁和阀杆 24的外侧壁，二者 之一可以设置安装槽， 安装槽内设有密封圈 271。 密封圈 271使得阀座和 阀杆 24之间具备良好的密封性能， 而且，相较于背景技术中通过碗状塑料 片密封的方式， 本实施例中的密封圈 271能够实现双向密封， 无论冷媒流 向如何， 均可以保持较好的密封效果。
当阀座包括阀芯座 26和阀座基体 25 ,阀口 251开设于阀座基体 25上 , 阀芯座 26插装于阀座基体 25内， 轴向通孔设于阀芯座 26 , 如图 4所示， 此时可以将阀芯座 26的轴向通孔设置为台阶孔， 台阶孔形成朝向阀壳 21 的环形台阶面 261。
电子膨胀阀还可以包括限位套 29, 限位套 29插入台阶孔， 如图 3所 示， 限位套 29的一端部具有环形的径向凸台， 限位套 29的具体结构可以 参考图 10-11理解， 图 10为图 3中阀杆与限位套的装配示意图； 图 11为 图 10中各部件装配后的结构示意图。
限位套 29的径向凸台搭接于阀芯座 26上朝向阀壳 21 的端面 (图 3 中的上端面）； 此时， 阀芯座 26内侧壁 (台阶的内侧壁）、 限位套 29的朝 向阀口 251的端面和环形台阶面 261形成安装槽， 如图 12所示， 图 12为 图 3中 A部位的局部放大示意图。 限位套 29与阀芯座 26配合后能够形成 安装槽， 密封圈 271可以置于该安装槽内。 该种结构便于密封圈 271的安 装， 阀杆 24可以先装配入阀芯座 26内， 再依次装入密封圈 271和限位套 29; 或者， 如图 11所示， 将密封圈 271、 限位套 29和阀杆 24配合后， 整 体装入阀芯座 26。 当然， 安装槽设置于阀杆 24上也是可以的， 鉴于阀杆 24的强度和设计需求， 设于阀座上为较为优选的方式。
进一步地， 密封圈 271和环形台阶面 261之间可以设有挡圈 28, 阀芯 座 26小径孔的内侧壁与阀杆 24之间具有一定的装配间隙 δ。 当阀杆 24釆 取加工为上小下大的结构时， 该装配间隙 δ 可以容许直径偏大的阀杆 24 的下端通过， 从而满足阀杆 24的装配需求， 比如阀杆 24的结构为大径段 筒体 24b和小径段筒体 24a时， 该装配间隙 δ大于两部分的直径差， 从而 便于装配； 挡圈 28与阀杆 24可以小间隙配合， 此时， 挡圈 28的设置能够 防止由于存在装配间隙 δ ,密封圈 271在阀杆 24的往复运动中脱离安装槽。
釆用限位套 29和阀芯座 26配合形成安装槽时， 装配后的限位套 29 与阀芯座 26需保持相对固定，可以在装配后通过焊接、螺纹连接等方式实 现固定。 该实施例中的电子膨胀阀可以通过齿轮系统 23实现限位套 29与 阀芯座 26的固定。
如图 13-15所示， 图 13为图 3中齿轮系统的结构示意图； 图 14为图 3中阀杆的结构示意图；图 15为图 3中齿轮系统和阀杆配合的结构示意图。
电子膨胀阀可以包括驱动阀杆 24轴向移动的齿轮系统 23 , 齿轮系统 23包括齿轮 231和丝杆 233 , 电子膨胀阀的电机 22驱动齿轮系统 23的齿 轮 231转动， 齿轮 231转动时， 丝杆 233随之转动， 丝杆 233与阀杆 24 螺纹配合， 如图 3、 11所示， 阀杆 24周向定位后， 可以将丝杆 233的转动 转化为阀杆 24的轴向移动。 为了实现阀杆 24的周向定位， 齿轮系统 23 还可以包括限制阀杆 24周向转动的限位杆 232 , 如图 15所示， 阀杆 24的 上端设有卡扣 241 , 卡扣 241的凸台 241a卡入两限位杆 232之间， 由于限 位杆 232的位置固定， 则卡扣 241无法转动，从而限制了阀杆 24的周向转 动， 仅能作轴向移动。 此时， 齿轮系统 23的限位杆 232可以将限位套 29压紧于阀芯座 26 的上端面上， 如图 3所示。 因此， 该结构利用齿轮系统 23 的限位杆 232 压紧限位套 29, 实现限位套 29和阀芯座 26的固定， 结构简单， 且易于装 配和拆卸， 使得限位套 29、 密封圈 271等构件的更换十分简便。
优选地， 电子膨胀阀还包括设于安装槽内的环形助滑片 272, 请继续 参考图 10、 12, 助滑片 272与阀杆 24外侧壁接触， 密封圈 271处于助滑 片 272和阀芯座 26的内侧壁之间。第一接口和第二接口存在压力差时，压 力使密封圈 271挤压变形， 助滑片 272能够捕捉到密封圈 271的挤压力， 从而紧紧贴合在阀杆 24光洁的外壁， 因此， 不管第一接口高压还是第二接 口高压， 均可以保证不泄漏， 而且相较于密封圈 271直接接触阀杆 24, 助 滑片 272大大减小了阀杆 24的轴向移动摩擦阻力。 因此，助滑片 272的设 置兼顾了密封和滑动性能。
助滑片 272的截面可以呈 C形， 且 C形开口朝向密封圈 271 , C形助 滑片 272的弧度有利于阀杆 24的装配导向， 因为 C形助滑片 272与密封 圈 271表面相配合， 从而避免装配时助滑片 272与密封圈 271相对滑移。 而且， 如此设计使得助滑片 272易于感知密封圈 271的变形量； 此外， 助 滑片 272与阀杆 24的接触面积相对较小， 进一步降低阀杆 24轴向移动时 的摩擦阻力。
助滑片 272的厚度可以处于 0.2〜0.6mm之间， 该厚度的助滑片 272能 够更为灵敏地感知密封圈 271的变形量， 以便贴紧阀杆 24, 确保密封性。 为了进一步减小摩擦系数， 助滑片 272 的材料中可以含有聚四氟乙烯 ( PTFE ), 当然， 助滑片 272釆用一般的塑料材料制成也是可以的。
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 了具体个例对本发明的原理及实施方式进行了阐述， 以上实施例的说明只 是用于帮助理解本发明的方法及其核心思想。 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， 其阀腔中设有阀杆（24 ), 所述阀杆（24 ) 能够
( 251 ), 以便导通或断开电子膨胀阀的两个接口， 其特征在于， 所述阀杆 ( 24 )设有连通阀口的轴向通孔，所述阀座的轴向通孔侧壁与所述阀杆（ 24 ) 密封； 所述阀杆（24 )的端面包括能够与阀座上位于所述阀口 （251 )处的 端面接触密封的密封面， 所述密封面包括用于承受一接口冷媒作用力的第 一密封面和与用于承受另一接口冷媒作用力的第二密封面， 且所述第一密 封面和所述第二密封面的有效承压面积相等。
2、 如权利要求 1所述的电子膨胀阀， 其特征在于， 所述阀杆（24 )为 圓筒状体， 所述阀杆（24 ) 包括小径段筒体（24a )和靠近阀口 （251 ) 的 大径段筒体（24b ); 所述大径段筒体（24b )的端面包括所述第一密封面和 所述第二密封面。
3、 如权利要求 2 所述的电子膨胀阀， 其特征在于， 所述大径段筒体 ( 24b )端面的外环线直径大于或等于所述阀口处密封面的外环线直径； 内 环线小于所述阀口处密封面的内环线直径；
且满足下述关系式：
Dl~ ( D3+D4 ) /2;
其中， D1为小径段筒体的外径、 D3为阀口处密封面的外环线直径、 D4为阀口处密封面的内环线直径。
4、 如权利要求 3所述的电子膨长阀， 其特征在于， 所述阀口处密封面 的外环线直径和内环线直径满足下述关系式：
0.4mm<D3 -D4<4mm。
5、 如权利要求 3 所述的电子膨胀阀， 其特征在于， 所述大径段筒体 ( 24b ) 的端部和 /或所述阀座上设置所述阀口 （251 ) 的一端设置有倒角。
6、 如权利要求 1-5任一项所述的电子膨胀阀， 其特征在于， 所述阀座 包括阀芯座（ 26 )和阀座基体 ( 25 ), 两所述接口和所述阀口 （ 251 ) 均开 设于所述阀座基体（ 25 )上， 所述阀芯座 ( 26 )插装于所述阀座基体 ( 251 ) 内， 所述轴向通孔设于所述阀芯座 ( 26 )。 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（26) 开设有与一所述接口连通的侧孔（262), 所述侧孔（262)的宽度沿背离所 述阀口的方向渐增， 当所述阀杆（24)沿轴向移动脱离阀口 （251 )时， 与 所述侧孔（ 262 )连通的所述接口能够通过所述侧孔（ 262 )与所述阀口（ 251 ) 连通； 另一所述接口与所述阀口（251)连通。
8、 如权利要求 1-5任一项所述的电子膨胀阀， 其特征在于， 所述阀座 轴向通孔的内侧壁和所述阀杆（24) 的外侧壁， 二者之一设有安装槽， 所 述安装槽内设有密封圈 （271)。
9、 如权利要求 8所述的电子膨胀阀， 其特征在于， 所述阀座包括阀芯 座（26)和阀座基体（25), 所述阀芯座（26)插装于所述阀座基体 (251 ) 内， 所述轴向通孔设于所述阀芯座（26); 所述阀芯座（26)的所述轴向通 孔为台阶孔， 台阶孔形成朝向电子膨胀阀阀壳（ 21 )的环形台阶面 ( 261 ); 还包括限位套 ( 29 ), 所述限位套 ( 29 )插入所述台阶孔， 所述限位套 ( 29 )的一端部具有环形的径向凸台，所述径向凸台搭接于所述阀芯座（ 26 ) 朝向所述阀壳（21 )的端面； 所述阀芯座（26) 内侧壁、 所述限位套（29) 上朝向所述阀口 （251 )的端面， 以及所述环形台阶面（261 )形成安装槽。
10、如权利要求 9所述的电子膨胀阀，其特征在于，所述密封圈 ( 271 ) 和所述环形台阶面 （261 )之间设有挡圈 （28), 所述阀芯座（26) 台阶孔 的小径段侧壁与所述阀杆（24)具有装配间隙； 所述挡圈 （28) 与所述阀 杆（24) 间隙配合。
11、 如权利要求 9所述的电子膨胀阀， 其特征在于， 还包括驱动所述 阀杆（24)轴向移动的齿轮系统（23), 所述齿轮系统（23) 包括限制所述 阀杆（24)周向转动的限位杆（232); 所述限位杆（232)压紧所述限位套
(29) 于所述阀芯座（26)上。
12、 如权利要求 9所述的电子膨胀阀， 其特征在于， 还包括设于所述 安装槽内的呈环形的助滑片 （272), 所述助滑片 （272)与所述阀杆（24) 外侧壁接触，所述密封圈（271 )处于所述助滑片（272)和所述阀芯座（26) 的内侧壁之间。
13、如权利要求 12所述的电子膨胀阀 ,其特征在于，所述助滑片（ 272 ) 的截面呈 C形， 且 C形开口朝向所述密封圈 （271)。
14、如权利要求 12所述的电子膨胀阀，其特征在于，所述助滑片 ( 272 ) 的厚度处于 0.2〜0.6mm之间。
15、如权利要求 12所述的电子膨胀阀，其特征在于，所述助滑片 ( 272 ) 的材料包括聚四氟乙烯。
16、 一种电子膨月长阀， 其阀腔中设有阀杆（24), 所述阀杆（24)能够
(251 ), 以便导通或断开电子膨胀阀的两个接口， 其特征在于， 所述阀杆 (24)设有连通阀口的轴向通孔； 所述阀杆（24) 关闭所述阀口时， 与所 述阀座线接触；
一所述接口的冷媒作用于所述阀杆（24)的上、 下有效承压面积相等; 另一所述接口的冷媒作用于所述阀杆（24) 的上、 下有效承压面积相等。
17、 如权利要求 16所述的电子膨胀阀， 其特征在于， 所述阀杆为圓筒 状体， 所述阀杆（24) 包括小径段筒体和靠近阀口 （251 ) 的大径段筒体； 大径段筒体具有雉端， 所述雉端能够与所述阀座线接触； 所述阀座上与所 述雉端线接触时形成的密封环线的直径与小径段筒体直径相等。
PCT/CN2013/076411 2012-12-11 2013-05-29 电子膨胀阀 Ceased WO2014089953A1 (zh)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP13862253.5A EP2933540B1 (en) 2012-12-11 2013-05-29 Electronic expansion valve
JP2015545637A JP6136035B2 (ja) 2012-12-11 2013-05-29 電子膨張弁
KR1020157018084A KR101684637B1 (ko) 2012-12-11 2013-05-29 전자 팽창밸브
US14/650,276 US9890869B2 (en) 2012-12-11 2013-05-29 Electronic expansion valve

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201210537711.3 2012-12-11
CN201210537711.3A CN103868289B (zh) 2012-12-11 2012-12-11 电子膨胀阀
CN201210538834.9 2012-12-11
CN201210538834.9A CN103867732B (zh) 2012-12-11 2012-12-11 电子膨胀阀

Publications (1)

Publication Number Publication Date
WO2014089953A1 true WO2014089953A1 (zh) 2014-06-19

Family

ID=50933759

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2013/076411 Ceased WO2014089953A1 (zh) 2012-12-11 2013-05-29 电子膨胀阀

Country Status (5)

Country Link
US (1) US9890869B2 (zh)
EP (1) EP2933540B1 (zh)
JP (1) JP6136035B2 (zh)
KR (1) KR101684637B1 (zh)
WO (1) WO2014089953A1 (zh)

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6134287B2 (ja) * 2014-03-31 2017-05-24 株式会社コガネイ 絞り弁
JP6771463B2 (ja) * 2014-11-29 2020-10-21 エアロジェット ロケットダイン インコーポレイテッド 電子制御されるバルブアセンブリ
CN106439072B (zh) * 2015-08-11 2019-04-02 浙江三花制冷集团有限公司 一种电子膨胀阀
JP1589530S (zh) * 2016-09-22 2017-10-30
WO2018079586A1 (ja) * 2016-10-26 2018-05-03 株式会社フジキン 流量調整弁およびこれを用いた流体制御装置
USD842969S1 (en) * 2017-01-11 2019-03-12 Zhejiang Sanhua Automotive Components Co., Ltd. Electronic expansion valve
CN109723877B (zh) * 2017-10-27 2021-06-18 浙江三花制冷集团有限公司 一种电动阀
KR102058114B1 (ko) 2018-01-15 2019-12-20 그린산업 주식회사 전자식 팽창밸브
KR102408886B1 (ko) 2018-01-31 2022-06-14 저장 산후아 클라이메이트 앤드 어플라이언스 컨트롤스 그룹 컴퍼니 리미티드 밸브 코어 조립체
KR102763265B1 (ko) * 2018-05-22 2025-02-07 컴파트 시스템즈 피티이. 엘티디. 가변 제어 오리피스 밸브
CN209196130U (zh) * 2018-08-02 2019-08-02 浙江盾安禾田金属有限公司 空调及其电子膨胀阀
KR102237186B1 (ko) * 2019-09-20 2021-04-07 (주)엔투텍 진공 게이트 밸브
ES2967628T3 (es) * 2019-12-20 2024-05-03 Danfoss As Válvula de expansión
KR102462772B1 (ko) * 2021-03-23 2022-11-03 엘지전자 주식회사 팽창밸브
CN113309859B (zh) * 2021-07-05 2024-12-06 多立恒（北京）能源技术股份公司 一种阀门
KR20240056601A (ko) * 2021-09-30 2024-04-30 제지앙 둔안 아트피셜 인바이런먼트 컴퍼니 리미티드 전자 팽창 밸브
EP4450854A4 (en) * 2021-12-18 2025-03-26 Zhejiang Dunan Artificial Environment Co., Ltd. VALVE ARRANGEMENT, SHUT-OFF VALVE AND COOLING SYSTEM
CN116518094A (zh) * 2022-01-20 2023-08-01 广东威灵电机制造有限公司 电子膨胀阀、制冷设备及汽车
CN114517755A (zh) * 2022-02-16 2022-05-20 一汽解放汽车有限公司 一种开关阀及供油系统
CN115026569B (zh) * 2022-06-09 2023-11-03 东莞市振亮精密科技有限公司 电子膨胀阀组装设备
KR102697136B1 (ko) * 2024-01-26 2024-08-22 엠티에이치콘트롤밸브(주) 유량 조절밸브

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4556193A (en) * 1983-09-30 1985-12-03 Fuji Koki Manufacturing Co., Ltd. Motor-driven expansion valve
JPH10311434A (ja) * 1997-05-09 1998-11-24 Toshiba Corp 流量制御弁および冷凍サイクル
JP2000227165A (ja) * 1999-02-05 2000-08-15 Saginomiya Seisakusho Inc 電動式コントロールバルブ
JP2001241562A (ja) * 2000-03-01 2001-09-07 Pacific Ind Co Ltd 制御弁
CN102644785A (zh) * 2011-02-17 2012-08-22 浙江三花股份有限公司 一种电子膨胀阀

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3001551A (en) * 1958-09-16 1961-09-26 Wyser Walter Valve for radiators and the like
US3918726A (en) * 1974-01-28 1975-11-11 Jack M Kramer Flexible seal ring
US4285498A (en) * 1976-05-17 1981-08-25 Imperial Chemical Industries Limited Control valves
JPH083789Y2 (ja) 1987-10-07 1996-01-31 太平洋工業株式会社 電動弁の構造
JP3150885B2 (ja) 1995-09-18 2001-03-26 太平洋工業株式会社 制御弁
US6568656B1 (en) 1998-07-09 2003-05-27 Sporlan Valve Company Flow control valve with lateral port balancing
US6460567B1 (en) * 1999-11-24 2002-10-08 Hansen Technologies Corpporation Sealed motor driven valve
JP2001280728A (ja) 2000-03-30 2001-10-10 Sumitomo Heavy Ind Ltd 冷凍機、直動機構、ロータリバルブ
JP2001280535A (ja) 2000-03-31 2001-10-10 Saginomiya Seisakusho Inc 電動式コントロールバルブ
JP4316788B2 (ja) 2000-11-27 2009-08-19 株式会社鷺宮製作所 双方向型電磁弁および空気調和機
US6568565B1 (en) 2001-04-04 2003-05-27 Lancer Partnership, Ltd. Method and apparatus for dispensing product
CN2483564Y (zh) 2001-05-18 2002-03-27 钟淑芬 缓开式活塞阀
KR100835259B1 (ko) 2007-02-23 2008-06-05 자화전자 주식회사 다방향 전자팽창밸브
CN202109047U (zh) * 2011-06-27 2012-01-11 浙江三花股份有限公司 一种流量调节阀
CN103512287B (zh) 2012-06-15 2016-09-07 浙江三花股份有限公司 一种电子膨胀阀

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4556193A (en) * 1983-09-30 1985-12-03 Fuji Koki Manufacturing Co., Ltd. Motor-driven expansion valve
JPH10311434A (ja) * 1997-05-09 1998-11-24 Toshiba Corp 流量制御弁および冷凍サイクル
JP2000227165A (ja) * 1999-02-05 2000-08-15 Saginomiya Seisakusho Inc 電動式コントロールバルブ
JP2001241562A (ja) * 2000-03-01 2001-09-07 Pacific Ind Co Ltd 制御弁
CN102644785A (zh) * 2011-02-17 2012-08-22 浙江三花股份有限公司 一种电子膨胀阀

Also Published As

Publication number Publication date
KR101684637B1 (ko) 2016-12-08
EP2933540A4 (en) 2016-09-07
KR20150095754A (ko) 2015-08-21
US20150316168A1 (en) 2015-11-05
JP2016505777A (ja) 2016-02-25
US9890869B2 (en) 2018-02-13
JP6136035B2 (ja) 2017-05-31
EP2933540A1 (en) 2015-10-21
EP2933540B1 (en) 2020-12-16

Similar Documents

Publication Publication Date Title
WO2014089953A1 (zh) 电子膨胀阀
JP5510685B2 (ja) 電動弁
EP3792529A1 (en) Valve needle assembly and electronic expansion valve having the valve needle assembly
US11313485B2 (en) Electric valve and manufacturing method thereof
US11054042B2 (en) Eccentric butterfly valve
KR20170128087A (ko) 버터플라이 밸브
JP5710081B2 (ja) バルブ
WO2014068765A1 (ja) バルブ
CN204862722U (zh) 双向密封对接阀及咖啡机
CN219841044U (zh) 电子膨胀阀、具有其的热管理系统和车辆
WO2019139004A1 (ja) バタフライバルブ
WO2022007589A1 (zh) 一种电动阀及电动阀的装配方法
CN103867732B (zh) 电子膨胀阀
US11193596B2 (en) Electric valve and manufacturing method therefor
CN110553070A (zh) 一种动态平衡二通阀
CN103383012B (zh) 止回阀
JP2024543506A (ja) 止め弁
EP2447512B1 (en) Bypass air volume control system for throttle body
CN103868289B (zh) 电子膨胀阀
CN104613185B (zh) 电子膨胀阀
CN220505806U (zh) 阀门
KR20120102302A (ko) 분리형 밸브 시트 및 이를 이용한 라이징 스템 볼 밸브
JPWO2016121709A1 (ja) ライニング型バタフライバルブ
CN214197389U (zh) 一种阀门装置
CN216078529U (zh) 一种电磁阀

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: 13862253

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 14650276

Country of ref document: US

ENP Entry into the national phase

Ref document number: 2015545637

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 20157018084

Country of ref document: KR

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 2013862253

Country of ref document: EP