WO2015106724A1 - 一种直动式电动阀及其装配方法 - Google Patents

一种直动式电动阀及其装配方法 Download PDF

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Publication number
WO2015106724A1
WO2015106724A1 PCT/CN2015/071065 CN2015071065W WO2015106724A1 WO 2015106724 A1 WO2015106724 A1 WO 2015106724A1 CN 2015071065 W CN2015071065 W CN 2015071065W WO 2015106724 A1 WO2015106724 A1 WO 2015106724A1
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WO
WIPO (PCT)
Prior art keywords
valve
valve seat
rotor
nut
direct
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/CN2015/071065
Other languages
English (en)
French (fr)
Inventor
吕铭
魏先让
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 CN201410026132.1A external-priority patent/CN104791536B/zh
Priority claimed from CN201410025331.0A external-priority patent/CN104791544A/zh
Application filed by Zhejiang Sanhua Co Ltd filed Critical Zhejiang Sanhua Co Ltd
Priority to KR1020167009203A priority Critical patent/KR101823927B1/ko
Priority to KR1020187002550A priority patent/KR101843460B1/ko
Priority to EP15737429.9A priority patent/EP3098494B1/en
Priority to JP2016524052A priority patent/JP6219511B2/ja
Priority to US14/917,254 priority patent/US10352467B2/en
Publication of WO2015106724A1 publication Critical patent/WO2015106724A1/zh
Anticipated expiration legal-status Critical
Priority to US15/919,158 priority patent/US20180202570A1/en
Ceased legal-status Critical Current

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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
    • 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
    • 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
    • F16K1/02—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 with screw-spindle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • 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
    • F16K31/44—Mechanical actuating means
    • F16K31/50—Mechanical actuating means with screw-spindle or internally threaded actuating means
    • F16K31/508—Mechanical actuating means with screw-spindle or internally threaded actuating means the actuating element being rotatable, non-rising, and driving a non-rotatable axially-sliding element
    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves

Definitions

  • the invention relates to the technical field of fluid control components, and in particular to a direct-acting electric valve. Furthermore, the invention relates to an assembly method for assembling the direct-acting electric valve.
  • a flow control valve is required on each refrigerant circuit of the indoor unit to cut off the refrigerant or adjust the flow rate.
  • the flow control valve is required to be able to adjust the flow rate of any opening degree, and the operation is stable, and since the refrigerant circuit of each indoor unit needs to be installed, the flow control valve is required to meet the requirements of miniaturization and large capacity.
  • the flow control valve mostly adopts a pilot-operated control valve, and the pilot valve core is driven by the motor, and the main valve core is opened and closed by the main valve core and the pilot valve core.
  • the pilot control valve opens the main valve port, the opening area increases suddenly and the flow rate changes abruptly, that is, the pilot control valve cannot precisely adjust the flow rate.
  • a direct-acting control valve In order to accurately adjust the flow rate of the refrigerant, a direct-acting control valve can be used.
  • the utility model relates to a direct-acting control valve.
  • the output shaft of the motor is connected with the screw drive through a gear system.
  • the screw rod is connected with a nut through a threaded joint, the nut is connected with the valve core, and the nut is limited, only along its axis. Sliding, can not rotate in the circumferential direction; when working, the motor starts, its output shaft rotates, and is transmitted to the screw through the gear system.
  • the nut slides in the axial direction, thereby driving the spool along the axial direction. Sliding, thereby achieving the purpose of adjusting the opening of the valve port.
  • valve port area of the flow control valve is required. Large, and thus the required driving force is large. If the above-mentioned direct-acting control valve is used, in order to obtain a large driving force, the size of the motor is inevitably increased, so that the volume of the control valve is too large, which not only increases the cost but also handles loading and unloading. bring inconvenience.
  • Another type of direct-acting control valve is provided, the screw rod is fixed to the rotor of the motor, and the nut is matched by a screw, and the lower end of the screw rod is directly matched with the valve core, and the nut and the valve seat are fixed; when working, the rotor of the motor is driven The screw rotates. Because the screw and the nut are threaded and the nut is fixed, the rotor also drives the screw to move axially, thereby driving the spool to open or close the valve port.
  • An object of the present invention is to provide a direct-acting electric valve capable of driving a valve spool to open and close a large-diameter valve port with a motor of a small size, thereby meeting the requirements of miniaturization and large capacity.
  • the present invention provides a direct-acting electric valve including a valve seat having a valve chamber, a motor disposed at an upper end of the valve seat, and a screw rod; the screw rod is connected with a nut by a screw fit.
  • the nut is connected with a valve core; the axial position of the rotor of the motor and the valve seat is fixed, and the upper end of the screw rod is fixedly connected with the rotor, and the valve core can be driven by the nut
  • the valve chamber is axially moved to open or close a valve port provided on the valve seat;
  • the valve core is a cylindrical structure having a balance passage, and an outer circumference thereof is provided to divide the valve chamber into two independent chambers Body seal.
  • the coil component of the motor drives the rotor to rotate. Since the axial position of the rotor and the valve seat is fixed, and the screw rod is fixedly connected with the rotor, the rotor only drives the screw to rotate, and the nut threaded with the screw thread will wire.
  • the rotation of the rod is converted into an axial movement, thereby driving the spool to move axially to open or close the valve port;
  • the above structure eliminates the gear system, reduces unnecessary transmission, thereby reducing power loss, and the response is directly reliable and sensitive;
  • the axial position of the rotor and the valve seat is fixed, that is, the relative position of the rotor and the coil component is fixed during operation, and the driving force of the motor is not It changes with the axial movement of the spool, and the spool has a balanced passage, and the resistance is small when the valve is opened.
  • the size of the motor of the present scheme is smaller than that of the background art, and Meet the requirements of miniaturization and large capacity.
  • the axial position of the rotor of the motor and the upper valve seat is relatively fixed, and the screw rod is fixedly connected with the rotor.
  • the motor directly drives the screw to rotate, and the nut matched with the screw thread converts the rotation of the screw rod into an axial movement.
  • driving the spool to move axially to open or close the valve port eliminating the gear system, reducing unnecessary transmission, small power loss, and more direct and reliable response;
  • the axial position of the rotor of the motor and the upper valve seat is relatively fixed, so that the relative position between the rotor and the coil component of the motor is fixed.
  • the driving torque of the motor does not change with the axial movement of the spool, and the foregoing Combined, it can effectively reduce the size of the motor.
  • the lead screw is welded and fixed to the rotor through an annular connecting piece; the periphery of the through hole of the annular connecting piece extends in the axial direction to form a protruding portion.
  • the rotor is a permanent magnet rotor; a ratio of an outer diameter of the rotor to a diameter of the valve port is 0.8 to 1.8.
  • the nut includes a small diameter portion and a large diameter portion that are threadedly engaged with the lead screw;
  • the upper end of the valve core has a receiving cavity for accommodating the large diameter portion of the nut, and the upper end of the inner wall of the receiving cavity is provided with an annular step with a step surface facing the screw rod, and a nut cover plate is disposed thereon to limit the nut And the relative position of the valve core in the axial direction.
  • the balance passage of the spool includes the receiving cavity, an axial through hole penetrating the receiving cavity, and a venting groove provided on a peripheral wall of the nut.
  • the lower end of the inner wall of the axial through hole is provided with an annular groove in which a filter mesh is disposed.
  • the bottom end of the valve core has an axial protrusion on which a sealing ring is riveted, and when the valve body is in a fully closed state, a lower end surface of the sealing ring is fitted to an end surface of the valve port Form a seal.
  • the axial centerline of the rotor coincides with the axial centerline of the coil component of the machine.
  • the invention also provides a method for assembling a direct-acting electric valve, comprising the following steps:
  • the direct-acting electric valve provided by the present invention adopts the assembling method of the above-mentioned direct-acting electric valve. Since the above-mentioned direct-acting electric valve has the above technical effects, the assembling method for assembling the direct-acting electric valve should also be provided. The corresponding technical effect.
  • the assembly of the upper valve seat assembly comprises the following steps:
  • a rotor of the motor is jacketed to the upper end of the upper valve seat and fixedly coupled to the lead screw.
  • FIG. 1 is a cross-sectional view showing a specific embodiment of a direct-acting electric valve according to the present invention, showing a structure in which the spool is in a fully open state;
  • FIG. 2 is a cross-sectional view showing a specific embodiment of a direct-acting electric valve according to the present invention, showing a structure in which the spool is in a fully closed state;
  • Figure 3 shows the balanced passage structure of the spool assembly when the spool is fully closed
  • Figure 4 is a schematic view showing the structure of the upper valve seat assembly of Figure 1.
  • Figure 5 is a cross-sectional view of the upper valve seat assembly of Figure 1;
  • Figure 6 is a plan view of Figure 5;
  • Figure 7 is a schematic structural view of the spool assembly of Figure 1;
  • Figure 8 is a cross-sectional view of the spool assembly of Figure 1;
  • Figure 9 is a plan view of Figure 8.
  • Figure 10 is a schematic structural view of the valve seat core of Figure 1;
  • Figure 11 is a schematic structural view of the lower valve seat of Figure 1;
  • Figure 12 is an enlarged schematic view of the upper chamber of the upper valve seat
  • Figure 13 is a schematic structural view of the upper valve seat
  • Figure 14 is a schematic structural view of a snap ring
  • Figure 15 is a flow chart showing the assembly of a direct-acting electric valve
  • Figure 16 is a flow chart showing the assembly of the valve seat assembly
  • Figure 17 shows a schematic flow diagram of assembling a spool assembly.
  • the core of the present invention is to provide a direct-acting electric valve that can open and close a large-diameter valve port by a small-sized motor to drive the valve core, thereby meeting the requirements of miniaturization and large capacity.
  • FIG. 1 is a cross-sectional view showing a specific embodiment of a direct-acting electric valve according to the present invention, showing a structure in which the valve core is in a fully open state;
  • FIG. 2 is a direct-acting type provided by the present invention.
  • a cross-sectional view of one embodiment of an electric valve showing the structure in which the spool is in a fully closed state.
  • the direct-acting electric valve includes a valve seat 30 having a valve chamber, a housing 20 coupled to the valve seat 30, a motor 10 disposed at an upper end of the valve seat 30, and a lead screw 312; wherein the screw shaft 312 is threadedly engaged A nut 41 is connected, and a nut 42 is connected to the valve core 42.
  • the rotor 12 of the motor 10 is disposed in the outer casing 20 and is fixed relative to the axial position of the valve seat 30.
  • the coil component 11 is sheathed to the outer casing 20, and the upper end of the screw 312 is
  • the rotor 12 is fixedly connected, and the valve core 42 can be axially moved along the valve chamber under the driving of the nut 41 to open or close the valve port 30a provided on the valve seat 30; wherein the valve core 42 is a tubular shape with a balanced passage
  • the structure is peripherally provided with a seal that separates the valve chamber into two separate chambers.
  • the direct-acting electric valve includes a spool assembly 400 and a lower valve seat assembly 302; wherein the lower valve seat assembly 302 includes a lower valve seat 32 and a valve seat core 321 disposed in a cavity of the lower valve seat 32; the spool assembly 400 includes a nut 41 and a valve core 42 connected to the nut 41; further comprising an upper valve seat assembly 301, further comprising an upper valve seat 31, a lead screw 312 and a rotor 12 of the motor 10; the upper valve seat 31 and the lower valve seat 32 are fixedly connected, and two The inner cavity of the person is connected; the rotor 12 is jacketed on the upper end of the upper valve seat 31, and the upper valve seat The axial position of 31 is relatively fixed; the upper end of the screw 312 is fixedly connected to the rotor 12 through the upper valve seat 31, and the lower end is threadedly engaged with the nut 41.
  • the valve core 42 can be driven along the core cavity of the valve seat core 321 by the nut 41. The axial
  • the axial position of the rotor 12 of the motor 10 and the upper valve seat 31 are relatively fixed, and the screw rod 312 is fixedly connected with the rotor 12.
  • the motor 10 directly drives the screw 312 to rotate, and the nut 41 threadedly engaged with the screw rod 312 is wire.
  • the rotation of the rod 312 is converted into an axial movement, thereby driving the spool 42 to move axially to open or close the valve port 32a, eliminating the gear system, reducing unnecessary transmission, small power loss, and more direct and reliable response;
  • the axial position of the rotor 12 of the motor 10 and the upper valve seat 31 are relatively fixed, so that the relative position between the rotor 12 and the coil component 11 of the motor 10 is fixed, and the driving torque of the motor 10 does not follow the spool 42 during operation.
  • the axial movement varies, and in combination with the foregoing, the size of the motor 10 can be effectively reduced.
  • the upper valve seat 31 is jacketed with a casing 20, and the coil component 11 of the motor 10 is sheathed to the casing 20 and supported by a mounting bracket 21 that is sleeved on the casing 20.
  • the coil component 11 of the motor 10 drives the rotor 12 to rotate. Since the axial position of the rotor 12 and the valve seat 30 is fixed, and the screw rod 312 is fixedly coupled to the rotor 12, the rotor 12 only drives the screw 312 to rotate.
  • the nut 41 threadedly engaged with the screw 312 converts the rotation of the screw 312 into an axial movement, thereby driving the spool 42 to move axially to open or close the valve port 30a; the above structure eliminates the gear system and reduces unnecessary The transmission reduces the power loss, the response is directly reliable and sensitive; and the axial position of the rotor 12 and the valve seat 30 is relatively fixed, that is, the relative position of the rotor 12 and the coil component 11 is fixed during operation, and the driving force of the motor 10 is not The change with the axial movement of the valve body 42 is obvious.
  • the motor of the present embodiment is smaller in size than the background art, and can meet the requirements for miniaturization and large capacity of the valve body.
  • the axial centerline of the rotor 12 coincides with the axial centerline of the coil member 11; in a preferred embodiment, the axial centerline of the coil member 11, the axial centerline of the bearing 311, and the axial direction of the rotor 12.
  • the center lines are coincident; thus, the driving force of the motor 10 can be maximized.
  • valve seat 30 includes an upper valve seat 31 and a lower valve seat 32, and the two are fixedly connected; wherein the valve port 30a is disposed at the lower valve seat 32.
  • FIG. 4 is a schematic structural view of the upper valve seat assembly of FIG. 1
  • FIG. 5 is a cross-sectional view of the upper valve seat assembly of FIG. 1
  • FIG. 6 is a top view of FIG.
  • the upper valve seat 31 includes a small diameter section and a large diameter section that are inserted into the interior of the rotor 12, and the screw shaft 312 is fixedly coupled to the rotor 12 through the inner cavity of the upper valve seat 31.
  • the screw rod 312 is welded and fixed to the rotor 12 through the annular connecting piece 315; the annular connecting piece 315 has an annular shape, and the intermediate through hole can be jacketed on the screw rod 312.
  • the outer side of the annular connecting piece 312 is welded and fixed to the rotor 12, The strength of the connection of the screw 312 to the rotor 12 is ensured.
  • the periphery of the through hole of the annular connecting piece 315 extends in the axial direction to form a protruding portion; thus, the protruding portion is fitted to the screw rod 312, and the contact area of the annular connecting piece 315 and the screw rod 312 can be increased, thereby reinforcing the screw rod 312 and The strength of the connection between the rotors 12 ensures that the lead screw 312 can be rotated by the rotor 12.
  • the annular connecting piece 315 can be integrated with the rotor 12 to facilitate assembly.
  • the inner cavity of the upper valve seat 31 is divided into an upper cavity and a lower cavity by an annular plate.
  • the annular plate may be integrated with the upper valve seat 31.
  • the upper cavity is provided with a bearing 311, and the inner ring of the bearing 311 and the screw
  • the outer peripheral wall of the 312 is fitted, and the outer ring is fitted to the inner wall of the upper chamber.
  • the screw rod 312 is relatively fixed by the axial position of the bearing 311 and the upper valve seat 31, so that the axial direction of the rotor 12 and the upper valve seat 31
  • the position is relatively fixed, i.e., the above structure of the upper valve seat 31 determines the relative positions of the bearing 311, the screw 312, and the rotor 12.
  • the balance wall 31d may be disposed on the peripheral wall of the upper valve seat 31.
  • the balance hole 31d may be disposed on the small diameter section of the upper valve seat 31 for balancing the pressure and reducing the rotational resistance of the screw 312.
  • the upper end of the bearing 311 is further provided with a bushing 313 which is sleeved on the screw rod 312 and welded and fixed to the screw rod 312, so as to prevent the inner ring of the bearing 311 from being axially pressed with the outer ring of the bearing 311. Disengage.
  • a gasket 314 may also be jacketed on the bushing 313, and the gasket 314 may be welded to the upper end of the upper valve seat 31 to further prevent the inner and outer rings of the bearing 311 from being disengaged from each other.
  • the upper valve seat 31, the bearing 311, the lead screw 312, and the rotor 12 may be referred to as an upper valve seat assembly.
  • the upper end of the annular plate of the upper valve seat 31 is provided with a ring having a stepped surface facing the bearing 311.
  • the step 31f in this way, the friction of the contact with the annular plate directly when the inner ring of the bearing 311 is rotated can be avoided.
  • the threaded section of the screw 312 is located in the lower cavity of the upper valve seat 31.
  • the lower cavity includes a small diameter cavity 31a and a large diameter cavity 31b for guiding the nut 41 screwed to the screw shaft 312, the large diameter cavity 31b cooperates with the inner cavity of the lower valve seat 32 to form a valve cavity. That is to say, the lower cavity of the upper valve seat 31 provides a space for the axial movement of the valve core assembly 400 composed of the nut 41 and the valve core 42, and the structural arrangement of the upper valve seat 31 is such that the axial dimension of the valve body is reduced, which is advantageous for The valve body is miniaturized.
  • FIG. 7 is a schematic structural view of the valve core assembly of FIG. 1.
  • FIG. 8 is a schematic cross-sectional view of the valve core assembly of FIG. 1.
  • the spool assembly 400 includes a nut 41 and a valve body 42, wherein the nut 41 includes a small diameter portion 41a and a large diameter portion 41b that are threadedly engaged with the screw shaft 312, and an upper end of the valve body 42 has a receiving cavity that accommodates the large diameter portion 41b, An upper end of the inner wall of the accommodating chamber is provided with an annular step facing the rotor 12, and a nut cover 411 is disposed thereon to limit the relative positions of the nut 41 and the spool 42 in the axial direction.
  • the rotor 12 of the motor 10 can be rotated clockwise or counterclockwise under the driving of the coil component 11, so that the nut 41 can be moved up or down; in actual setting, the rotor 12 can be set clockwise.
  • the nut 41 is moved upward, and when the rotor 12 rotates counterclockwise, the nut 41 is moved downward; of course, when the rotor 12 rotates clockwise, the nut 41 is driven to move downward, and when the rotor 12 rotates counterclockwise, the nut is driven. 41 moves up.
  • the small-diameter portion 41a of the nut 41 extends into the small-diameter chamber 31a of the lower chamber of the upper valve seat 31.
  • the small-diameter portion 41a of the nut 41 moves axially along the small-diameter chamber 31a by the screw rod 312.
  • the small-diameter chamber 31a is opposed to the nut 41.
  • the axial movement acts as a guiding action to prevent the nut 41 from deflecting when moving in the axial direction, which affects the sealing performance of the valve core 42 to the valve port 30a.
  • a limiting member is also provided to limit the circumferential rotation of the nut 41.
  • the setting form of the limiting member can be various, and specifically to the solution, the nut 41 can be small
  • the diameter portion 41a is provided as a cylindrical structure having a non-circular cross section, such as a square column as shown in Fig. 7, and accordingly, the small diameter chamber 31a of the upper valve seat 31 is fitted with the square column.
  • the small-diameter portion 41a of the nut 41 may be disposed in a cross-sectional shape other than a non-circular cylindrical structure, such as a pentagon or the like, and the small-diameter cavity 31a may be fitted thereto, or may be in the small-diameter cavity 31a.
  • the inner wall is provided with a snap ring, the inner hole of the snap ring is non-circular, and the small diameter portion 41a of the nut 41 is disposed as a cylinder having a non-circular cross section in cooperation with the snap ring; in addition,
  • the bottom of the accommodating chamber is provided with a circumferential limiting groove, and the bottom of the large diameter portion 41b of the nut 41 is correspondingly disposed on the circumferential limiting protrusion of the circumferential limiting groove; the above is only used as a limiting member for restricting the circumferential rotation of the nut 41 Several examples.
  • the small-diameter cavity 31a of the upper valve seat 31 has a circular cross section, and the lower end of the cavity wall of the small-diameter cavity 31a is provided with an annular groove, and the annular groove is provided with a snap ring 316, and the snap ring 316 is provided.
  • the inner hole is a non-circular hole.
  • the inner hole of the snap ring 316 is a square hole.
  • the cross section of the small diameter section 41a of the nut 41 is matched with the inner hole of the snap ring 316. Thus, the nut can be restrained. 41 weeks of rotation.
  • FIG. 10 is a schematic structural view of the valve seat core of FIG. 1;
  • FIG. 11 is a schematic structural view of the lower valve seat of FIG.
  • a valve seat core 321 is fixed in the lower valve seat 32, the valve seat core 321 has a core cavity, and a peripheral wall thereof is provided with one or more flow regulating grooves 321a; the valve seat core 321 separates the valve cavity into a first cavity and surrounds The second cavity of the first cavity, obviously, the two cavities can communicate through the flow regulating groove 321a; it can be understood that the first cavity is the core cavity of the valve seat core 321; wherein the second cavity is The first nozzle 322 is in communication, and the first cavity is in communication with the second nozzle 323 through the valve port 30a.
  • the plurality of flow rate adjustment grooves 321a may be evenly arranged along the peripheral wall of the valve seat core 321.
  • the flow regulating groove 321a may be configured to have a circumferential length that tapers downward along the axial direction of the valve seat core 321, as shown in FIG. 10, which can make the flow rate adjustment of the refrigerant in a small flow range more precise.
  • the valve core 42 connected to the nut 41 is disposed in the valve cavity, specifically, in the first cavity.
  • the side wall of the valve core 42 can block the flow when the valve port 30a is closed.
  • the groove 321a is adjusted to cut off the communication between the first cavity and the second cavity, and when the valve core 42 is moved up by the nut 41, the flow regulating groove 321a is gradually opened, and the flow area of the flow regulating groove 321a is changed, thereby
  • the first cavity and the second cavity are connected to each other, and the flow rate of the refrigerant is adjusted. Obviously, it is necessary to maintain a seal between the spool 42 and the seat core 321 .
  • the core cavity of the valve seat core 321 is set as a stepped hole, the stepped hole forms a stepped surface facing the upper valve seat 31, and the upper end of the valve seat core 321 is inserted with an upper limit socket 421,
  • the upper end of the upper limit sleeve 421 has an annular radial boss that overlaps the valve seat core 321 toward the upper end surface of the upper valve seat 31.
  • the lower end surface of the upper limit sleeve 421 is toward the valve port 30a.
  • the end surface, the inner side wall of the valve seat core 12, and the stepped surface of the valve seat core 321 form a mounting groove, and a sealing ring 423 can be disposed in the mounting groove.
  • a lower limit sleeve 422 may be disposed between the seal ring 423 and the step surface of the valve seat core 321 . Since the spool 42 is generally configured to be large and small, to ensure the sealing of the valve port 30a, in order to meet the assembly requirements of the spool 42, there is an assembly gap between the small-diameter through hole of the valve seat core 321 and the spool 42. The setting of the lower limit sleeve 422 can prevent the seal ring 423 from coming off the mounting groove during the reciprocating motion of the spool due to the presence of the assembly gap.
  • the outer circumferential surface of the sealing ring 423 is provided with a sliding member 423a, and the sliding member 423a and the sealing ring 423 can be integrated, that is, the sliding member 423a is wrapped around the outer circumference of the sealing ring 423, or can be separately provided;
  • the pressure causes the sealing ring 423 to be pressed and deformed, and the sliding member 423a can be easily captured to the sealing ring 423 by being wrapped around the outer circumference of the sealing ring 423.
  • the pressing force is thereby fitted to the outer peripheral wall of the valve body 42 to ensure the sealing property, and the arrangement of the auxiliary slider 423a can also reduce the frictional resistance when the spool 42 is axially moved.
  • the upper limit sleeve 421 also needs to be relatively fixed with the valve seat core 321; in this embodiment, an axial convex portion may be disposed at the bottom of the large diameter section of the upper valve seat 31 to form a ring shape toward the lower valve seat 32.
  • the stepped surface, the upper valve seat 31 is inserted into the lower valve seat 32 through the axial convex portion, and the annular step surface is in contact with the upper end surface of the lower valve seat 32, and the lower end of the axial convex portion will be the upper limit socket 421
  • the upper end surface of the valve seat core 321 is pressed; further, the structural arrangement of the upper valve seat 31 is also easy to ensure its coaxiality with the lower valve seat 32.
  • the upper limit sleeve 421 and the valve seat core 321 can also be fixed by other means, such as welding or screwing.
  • the bottom end of the spool 42 has an axial projection on which the seal ring 425 is riveted.
  • the lower end surface of the seal ring 425 is fitted to the valve port 30a to form a seal. It is apparent that the outer end diameter of the seal ring 425 is larger than the diameter of the valve port 30a.
  • the rotor 12 of the motor 10 of the direct-acting electric valve is a permanent magnet rotor, specifically, a neodymium iron boron magnetic steel material or an anisotropic ferrite material, so that when the valve core 42 is in the fully closed state
  • the motor 10 is powered off, since the rotor 12 is a permanent magnet rotor, the motor 10 has a positioning torque in a power-off state, which can ensure the relative position between the screw 312 and the nut 41, thereby preventing the two from slipping.
  • the sealing property between the valve body 42 and the valve port 30a can be further ensured to prevent the occurrence of internal leakage.
  • the ratio of the outer diameter of the rotor 12 to the diameter of the valve port 30a is preferably 0.8 to 1.8.
  • valve core 42 has an axial through hole penetrating the receiving cavity
  • peripheral wall of the nut 41 has a venting groove 41c, that is, the balanced passage of the valve core 42 covers the accommodating cavity and the axial direction penetrating the accommodating cavity
  • the through hole and the venting groove 41c provided on the peripheral wall of the nut 41; thus, when the valve body 42 is in the fully closed state, the pressure at the upper and lower ends of the valve body 42 is balanced, which can be understood in conjunction with FIG. 3, and FIG. 3 shows the valve in the valve port fully closed state.
  • Schematic diagram of the pressure balance of the core assembly is shown in the valve port fully closed state.
  • the second nozzle 323 communicates with the axial through hole of the valve body 42 through the valve port 30a, and communicates with the large diameter chamber 31b of the upper valve seat 31 through the vent groove 41c of the nut 41, and the spool 42 receives
  • the differential pressure is small, and when the valve port 30a is opened, only a small driving force is required, that is, the smaller motor core 42 can be driven by the smaller motor 10, and the direct-acting electric valve can be further miniaturized.
  • the lower end of the inner wall of the axial through hole of the valve core 42 is provided with an annular groove in which the filter net 424 is disposed; the filter net 424 is disposed to prevent the impurities from being carried into the axial through hole of the valve body 42 when the refrigerant flows.
  • the thread that causes the screw 312 to engage with the nut 41 is stuck.
  • the small-diameter chamber 31a and the large-diameter chamber 31b of the lower chamber of the upper valve seat 31 of the direct-acting electric valve form a step end surface 31c facing the valve port 30a, and the distance between the step end surface 31c and the valve port 30a defines The axial movement distance of the spool 42.
  • the flow regulating groove 321a is fully opened, and the first connecting pipe 322 communicates with the second connecting pipe 323 through the flow regulating groove 321a.
  • the upper end surface of the valve body 42 and the step The end surface 31c abuts; as shown in FIG.
  • the direct-acting electric valve is capable of bidirectional circulation, and is understood in conjunction with FIGS. 1 and 2, the arrows in FIGS. 1 and 2 indicate the flow direction of the refrigerant; wherein the solid arrow indicates that the refrigerant flows in from the first nozzle 322, and the second nozzle The 323 flows out, and the dotted arrow indicates that the refrigerant flows in from the second nozzle 323, and the first nozzle 322 flows out.
  • Fig. 15 is a flow chart showing the assembly of a direct-acting electric valve.
  • the assembly method of the direct-acting electric valve includes the following steps:
  • the outer casing 20 and the holder 21 are press-fitted, and the coil component 11 of the motor 10 is assembled.
  • the assembly process of the upper valve seat assembly 301 can refer to FIG. 16 and includes the following steps:
  • the mounting gasket 314 is mounted on the upper end of the bearing 311 to be riveted or welded to the upper valve seat 31;
  • the bushing 313 is clamped between the screw rod 312 and the gasket 314 to abut against the upper end of the bearing 311 and welded to the screw rod 312;
  • the rotor 12 of the motor 10 is sheathed to the upper end of the upper valve seat 31 and fixedly coupled to the lead screw 312.
  • the assembly process of the spool assembly 400 can be referred to FIG. 17, and includes the following steps:
  • a filter 424 and a snap spring 425 are assembled.
  • the direct-acting electric valve provided by the present invention adopts the assembling method of the above-mentioned direct-acting electric valve. Since the above-mentioned direct-acting electric valve has the above technical effects, the assembling method for assembling the direct-acting electric valve should also have corresponding Technical effects. I won't go into details here.

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Abstract

一种直动式电动阀，包括具有阀腔的阀座（30）、设于阀座上端的电机（10）以及丝杆（312）；丝杆通过螺纹配合连接有螺母（41），螺母连接有阀芯（42）；电机的转子（12）和阀座的轴向位置相对固定，丝杆的上端与转子固定连接，阀芯在螺母的带动下能够沿阀腔轴向移动以开启或关闭设于阀座上的阀口（30a）；阀芯为具有平衡通道的筒状结构，且其外周设有将阀腔分隔为两个独立腔体的密封件。这种电动阀取消了齿轮系统，减少了不必要的传动，减少了摩擦损失，响应直接可靠且灵敏；而且转子与阀座的轴向位置固定，即工作过程中转子与线圈部件的相对位置固定，使得驱动力稳定，显然，对于同样大小的阀口，其电机尺寸相较于背景技术更小，能够满足小型化、大容量的要求。

Description

一种直动式电动阀及其装配方法
本申请要求于2014年01月20日提交中国专利局、申请号为201410026132.1、发明名称为“一种直动式电动阀”、于2014年01月20日提交中国专利局、申请号为201410025331.0、发明名称为“一种直动式电动阀及其装配方法”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，特别是涉及一种直动式电动阀。此外，本发明还涉及一种用于装配所述直动式电动阀的装配方法。
背景技术
多联机或模块机等商用空调，一个室外机联通多个室内机系统，每个室内机的冷媒回路上均需要安装流量控制阀，用于切断冷媒或调节流量大小。对该流量控制阀的要求为能够调节任意开度流量，动作稳定，又因为每个室内机的冷媒回路上均需安装，所以还需要该流量控制阀满足小型化、大容量的要求。
目前，所述流量控制阀多采用先导式控制阀，利用电动机驱动先导阀芯，由主阀芯与该先导阀芯联动地开闭主阀口。但是先导式控制阀在打开主阀口时，开口面积一下子增大，流量急剧变化，也就是说，先导式控制阀无法精确调节流量。
为了能够精确调节冷媒流量，可采用直动式控制阀。现有的一种直动式控制阀，电机的输出轴通过齿轮系统与丝杆传动连接，丝杆通过螺纹配合连接有螺母，螺母与阀芯连接，且螺母被限位，只能沿其轴向滑动，并不能沿周向旋转；工作时，电机启动，其输出轴发生转动，通过齿轮系统传递给丝杆，随着丝杆的转动，螺母沿轴向滑动，从而带动阀芯沿轴向滑动，进而实现调节阀口开度的目的。
由于在多联机或模块机等商用空调中，需要流量控制阀的阀口面积较 大，从而需要的驱动力较大，若采用上述直动式控制阀，为获得较大的驱动力，必然导致电机的尺寸增大，使得控制阀的体积过大，不仅增加成本，也给装卸带来不便。
现有的另一种直动控制阀，丝杆与电机的转子固定，并通过螺纹配合连接螺母，且丝杆的下端与阀芯直接配合，螺母与阀座固定；工作时，电机的转子驱动丝杆转动，由于丝杆与螺母螺纹配合，且螺母固定，所以转子还会带动丝杆轴向移动，从而带动阀芯开启或关闭阀口。然而，该种直动式控制阀工作时，由于转子轴向移动，从而转子与线圈部件的轴向中心位置发生变化，无法始终保持在线圈部件的轴向中心位置，进而降低驱动力，为开闭较大口径的阀口，也需要增加电机的尺寸。
有鉴于此，如何改进直动式控制阀，能够以较小尺寸的电机驱动阀芯开闭大口径的阀口，是本领域技术人员目前需要解决的技术问题。
发明内容
本发明的目的是提供一种直动式电动阀，能够以较小尺寸的电机驱动阀芯开闭大口径的阀口，从而满足小型化、大容量的要求。
为解决上述技术问题，本发明提供一种直动式电动阀，包括具有阀腔的阀座、设于所述阀座上端的电机以及丝杆；所述丝杆通过螺纹配合连接有螺母，所述螺母连接有阀芯；所述电机的转子和所述阀座的轴向位置固定，所述丝杆的上端与所述转子固定连接，所述阀芯在所述螺母的带动下能够沿所述阀腔轴向移动以开启或关闭设于所述阀座上的阀口；所述阀芯为具有平衡通道的筒状结构，且其外周设有将所述阀腔分隔为两个独立腔体的密封件。
如上设计，工作时，电机的线圈部件驱动转子转动，由于转子与阀座的轴向位置固定，且丝杆与转子固定连接，所以转子只带动丝杆转动，与丝杆螺纹配合的螺母将丝杆的转动转化为轴向移动，从而带动阀芯轴向移动，以开启或关闭阀口；上述结构取消了齿轮系统，减少了不必要的传动，从而减少了动力损失，响应直接可靠且灵敏；而且转子与阀座的轴向位置固定，即工作过程中转子与线圈部件的相对位置固定，电机的驱动力不会 随阀芯的轴向移动而变化，并，阀芯具有平衡通道，开阀时所受阻力较小，显然，对于同样大小的阀口，本方案的电机尺寸相较于背景技术更小，能够满足小型化、大容量的要求。
电机的转子与上阀座的轴向位置相对固定，且丝杆与转子固定连接，工作时，电机直接驱动丝杆转动，与丝杆螺纹配合的螺母将丝杆的转动转化为轴向移动，从而带动阀芯轴向移动以开启或关闭阀口，取消了齿轮系统，减少了不必要的传动，动力损失小，响应更直接可靠；
电机的转子与上阀座的轴向位置相对固定，使得转子与电机的线圈部件之间的相对位置固定，工作过程中，电机的驱动力矩不会随阀芯的轴向移动而变化，与前述结合，能够有效地减小电机的尺寸。
优选地，所述丝杆通过环形连接片与所述转子焊接固定；所述环形连接片的通孔周边沿轴向延伸形成突出部。
优选地，所述转子为永磁体转子；所述转子的外径与所述阀口的直径之比为0.8～1.8。
优选地，所述螺母包括与所述丝杆螺纹配合的小径部和大径部；
所述阀芯的上端具有容纳所述螺母大径部的容纳腔，所述容纳腔的内壁上端开设有台阶面朝向所述丝杆的环形台阶，其上设置螺母盖板，以限制所述螺母和所述阀芯在轴向上的相对位置。
优选地，所述阀芯的平衡通道包括所述容纳腔、与所述容纳腔贯通的轴向通孔以及设于所述螺母周壁的通气槽。
优选地，所述轴向通孔的内壁下端开设有环形槽，其内设置有过滤网。
优选地，所述阀芯的底端具有轴向凸出部，其上铆接有密封环，所述阀芯处于全关状态时，所述密封环的下端面与所述阀口的端面贴合形成密封。
优选地，所述转子的轴向中心线与所述电机的线圈部件的轴向中心线重合。
本发明还提供一种直动式电动阀的装配方法，包括如下步骤：
将组装好的阀芯组件安装于组装好的下阀座组件；
将组装好的上阀座组件的丝杆旋入所述阀芯组件的螺母，并将所述上 阀座组件的上阀座与所述下阀座组件的下阀座焊接固定；
压装外壳和固定架，并组装电机的线圈部件。
本发明所提供的直动式电动阀采用了上述直动式电动阀的装配方法，由于上述直动式电动阀具有上述技术效果，用于装配所述直动式电动阀的装配方法也应具备相应的技术效果。
优选地，所述上阀座组件的装配包括如下步骤：
压装丝杆、轴承和上阀座；
安装垫片于所述轴承上端，将其与所述上阀座铆接或焊接；
将衬套卡设于所述丝杆和所述垫片之间，使其与所述轴承的上端抵接，并与丝杆焊接固定；
将电机的转子外套于所述上阀座的上端，并与所述丝杆固定连接。
附图说明
图1为本发明所提供直动式电动阀一种具体实施方式的剖面图，示出了阀芯处于全开状态的结构；
图2为本发明所提供直动式电动阀一种具体实施方式的剖面图，示出了阀芯处于全关状态的结构；
图3示出了阀芯全关状态时阀芯组件的平衡通道结构；
图4为图1中上阀座组件的结构示意图
图5为图1中上阀座组件的剖面示意图；
图6为图5的俯视图；
图7为图1中阀芯组件的结构示意图；
图8为图1中阀芯组件的剖面示意图；
图9为图8的俯视图；
图10为图1中阀座芯的结构示意图；
图11为图1中下阀座的结构示意图；
图12为上阀座的上腔的放大示意图；
图13为上阀座结构示意图；
图14为卡环的结构示意图；
图15示出了装配直动式电动阀的流程示意图；
图16示出了装配上阀座组件的流程示意图；
图17示出了装配阀芯组件的流程示意图。
具体实施方式
本发明的核心是提供一种直动式电动阀，能够以较小尺寸的电机驱动阀芯开闭大口径的阀口，从而满足小型化、大容量的要求。
为了使本技术领域的人员更好地理解本发明方案，下面结合附图和具体实施方式对本发明作进一步的详细说明。
这里需要说明的是，本文中所涉及的上和下等方位词是以图1至图11中零部件位于图中及零部件相互之间的位置来定义的，只是为了表达技术方案的清楚及方便。应当理解，本文所采用的方位词不应限制本申请请求保护的范围。
请参考图1-2，图1为本发明所提供直动式电动阀一种具体实施方式的剖面图，示出了阀芯处于全开状态的结构；图2为本发明所提供直动式电动阀一种具体实施方式的剖面图，示出了阀芯处于全关状态的结构。
该实施例中，直动式电动阀包括具有阀腔的阀座30、与阀座30连接的外壳20、设于阀座30上端的电机10以及丝杆312；其中，丝杆312通过螺纹配合连接有螺母41，螺母41连接有阀芯42；电机10的转子12设于外壳20内，且与阀座30的轴向位置相对固定，线圈部件11外套于外壳20，丝杆312的上端与转子12固定连接，阀芯42在螺母41的带动下能够沿所述阀腔轴向移动以开启或关闭设于阀座30上的阀口30a；其中，阀芯42为具有平衡通道的筒状结构，其外周设有将所述阀腔分隔为两个独立腔体的密封件。
直动式电动阀包括阀芯组件400和下阀座组件302；其中，下阀座组件302包括下阀座32和设于下阀座32内腔的阀座芯321；阀芯组件400包括螺母41和与螺母41连接的阀芯42；还包括上阀座组件301，进一步包括上阀座31、丝杆312和电机10的转子12；上阀座31和下阀座32固定连接，且两者的内腔连通；转子12外套于上阀座31上端，且与上阀座 31的轴向位置相对固定；丝杆312的上端穿过上阀座31与转子12固定连接，下端与螺母41螺纹配合，阀芯42在螺母41的带动下能够沿阀座芯321的芯腔轴向移动以开启或关闭设于下阀座32的阀口32a。
该直动式电动阀具有如下技术效果：
电机10的转子12与上阀座31的轴向位置相对固定，且丝杆312与转子12固定连接，工作时，电机10直接驱动丝杆312转动，与丝杆312螺纹配合的螺母41将丝杆312的转动转化为轴向移动，从而带动阀芯42轴向移动以开启或关闭阀口32a，取消了齿轮系统，减少了不必要的传动，动力损失小，响应更直接可靠；
电机10的转子12与上阀座31的轴向位置相对固定，使得转子12与电机10的线圈部件11之间的相对位置固定，工作过程中，电机10的驱动力矩不会随阀芯42的轴向移动而变化，与前述结合，能够有效地减小电机10的尺寸。
其中，上阀座31外套有外壳20，电机10的线圈部件11外套于外壳20，并通过套设于外壳20的固定架21支撑。
如上设计，工作时，电机10的线圈部件11驱动转子12转动，由于转子12与阀座30的轴向位置固定，且丝杆312与转子12固定连接，所以转子12只带动丝杆312转动，与丝杆312螺纹配合的螺母41将丝杆312的转动转化为轴向移动，从而带动阀芯42轴向移动，以开启或关闭阀口30a；上述结构取消了齿轮系统，减少了不必要的传动，从而减少了动力损失，响应直接可靠且灵敏；而且转子12与阀座30的轴向位置相对固定，即工作过程中转子12与线圈部件11的相对位置固定，电机10的驱动力不会随阀芯42的轴向移动而发生变化，显然，对于同样大小的阀口30a，与背景技术相比，本方案的电机尺寸更小，能够满足阀体小型化、大容量的要求。
优选的方案中，转子12的轴向中心线与线圈部件11的轴向中心线重合；优选的方案中，线圈部件11的轴向中心线、轴承311的轴向中心线以及转子12的轴向中心线重合；如此，能够使电机10的驱动力最大化。
该实施例中，阀座30包括上阀座31和下阀座32，两者固定连接；其中，阀口30a设置于下阀座32。
请一并参考图4-6，图4为图1中上阀座组件的结构示意图；图5为图1中上阀座组件的剖面示意图；图6为图5的俯视图。
如图所示，上阀座31包括插入转子12内部的小径段和大径段，丝杆312穿过上阀座31的内腔与转子12固定连接。
具体的方案中，丝杆312通过环形连接片315与转子12焊接固定；环形连接片315呈环状，中间通孔，可外套于丝杆312，环形连接片312的外侧与转子12焊接固定，保证丝杆312与转子12的连接强度。
进一步地，环形连接片315的通孔周边沿轴向延伸形成突出部；如此，该突出部套装于丝杆312，可以增加环形连接片315与丝杆312的接触面积，从而增强丝杆312与转子12之间的连接强度，确保丝杆312能够在转子12的带动下转动。
具体的方案中，环形连接片315可与转子12设为一体结构，便于装配。
上阀座31的内腔被环形板分隔为上腔和下腔，该环形板可以与上阀座31设为一体，所述上腔内设置有轴承311，该轴承311的内圈与丝杆312的外周壁贴合，外圈与所述上腔的内壁贴合，如此，丝杆312通过轴承311与上阀座31的轴向位置相对固定，从而转子12与上阀座31的轴向位置相对固定，即上阀座31的上述结构确定了轴承311、丝杆312和转子12三者的相对位置。
其中，上阀座31的周壁还可开设平衡孔31d，该平衡孔31d可设于上阀座31的小径段，用于平衡压力，降低丝杆312的转动阻力。
进一步地，轴承311的上端还设置有衬套313，衬套313外套于丝杆312，并与丝杆312焊接固定，可以防止轴承311的内圈因受到轴向力而与轴承311的外圈脱开。还可在衬套313上外套垫片314，垫片314可与上阀座31的上端焊接，以进一步防止轴承311的内圈和外圈相互脱开。
上阀座31、轴承311、丝杆312和转子12可称为上阀座组件。
需要指出的是，上述仅作为示例给出了一种确定转子12和阀座30轴向位置的方式，实际中，还可通过其他方式将转子12和阀座30的轴向位置固定。
如图12所示，上阀座31环形板的上端设有台阶面朝向轴承311的环 形台阶31f；如此，可避免轴承311内圈转动时直接与环形板接触发生摩擦。
丝杆312的螺纹段位于上阀座31的下腔，所述下腔包括小径腔31a和大径腔31b，小径腔31a用于对与丝杆312螺纹连接的螺母41进行导向，大径腔31b与下阀座32的内腔配合形成阀腔。也就是说，上阀座31的下腔提供了螺母41和阀芯42组成的阀芯组件400轴向移动的空间，上阀座31的结构设置使得阀体的轴向尺寸减小，有利于阀体小型化设计。
请一并参考图7-图9，图7为图1中阀芯组件的结构示意图；图8为图1中阀芯组件的剖面示意图；图9为图8的俯视图。
阀芯组件400包括螺母41和阀芯42，其中，螺母41包括与丝杆312螺纹配合的小径部41a和大径部41b，阀芯42的上端具有容纳大径部41b的容纳腔，所述容纳腔的内壁上端开设有台阶面朝向转子12的环形台阶，其上设置有螺母盖板411，以限制螺母41和阀芯42在轴向上的相对位置。
当转子12转动，带动丝杆312转动，并带动螺母41向上移动时，由于螺母41大径部41b的端部与螺母盖板411发生干涉，从而能够带动阀芯42一起向上移动，避免螺母41脱离阀芯42。
当转子12转动，带动丝杆312转动，并带动螺母41向下移动时，螺母41可直接推动阀芯42一起向下移动，直至关闭阀口30a。
需要指出的是，电机10的转子12在线圈部件11的驱动下可顺时针转动或逆时针转动，从而能够带动螺母41上移或下移；在实际设置时，可以设定为转子12顺时针转动时，带动螺母41上移，转子12逆时针转动时，带动螺母41下移；当然也可以设定为转子12顺时针转动时，带动螺母41下移，转子12逆时针转动时，带动螺母41上移。
螺母41的小径部41a伸入上阀座31下腔的小径腔31a，在丝杆312的带动下，螺母41的小径部41a沿所述小径腔31a轴向移动，该小径腔31a对螺母41的轴向移动起到导向作用，避免螺母41在轴向移动时发生偏斜，影响阀芯42对阀口30a的密封性能。
显然，为确保螺母41能够将丝杆312的转动转化为轴向移动，以带动阀芯42轴向移动，还设置有限位件，以限制螺母41的周向转动。
限位件的设置形式可以为多种，具体到该方案中，可以将螺母41的小 径部41a设置为横截面为非圆形的柱体结构，如图7中所示的方形柱，相应地，上阀座31的小径腔31a与所述方形柱适配。当然，在实际设置时，也可以将螺母41的小径部41a设置为横截面为其他非圆形的柱体结构，如五边形等，小径腔31a与其适配，也可以在小径腔31a的内壁设置卡环，卡环的内孔设为非圆形，螺母41的小径部41a设置为与该卡环配合的横截面为非圆形的柱体；除此之外，还可以在所述容纳腔的底部设置周向限位槽，螺母41大径部41b的底部相应地设置于周向限位槽配合的周向限位凸起；以上仅作为限制螺母41周向转动的限位件的几种示例。
也可以采用图13所示，上阀座31的小径腔31a的横截面呈圆形，小径腔31a的腔壁下端设有环形槽，该环形槽内设置有卡环316，该卡环316的内孔为非圆形孔，图14中示出了卡环316内孔为方形孔的结构，螺母41的小径段41a的横截面与卡环316的内孔适配，如此，即可限制螺母41周向转动。
请一并参考图10-11，图10为图1中阀座芯的结构示意图；图11为图1中下阀座的结构示意图。
下阀座32内固设有阀座芯321，阀座芯321具有芯腔，且其周壁设置有一个或多个流量调节槽321a；阀座芯321将阀腔分隔为第一腔体和环绕第一腔体的第二腔体，显然，两个腔体可通过流量调节槽321a连通；可以理解，所述第一腔体即为阀座芯321的芯腔；其中，第二腔体与第一接管322连通，第一腔体通过阀口30a与第二接管323连通。
为了确保冷媒流量调节过程中，阀座芯321的受力稳定，多个流量调节槽321a可沿阀座芯321的周壁均匀布置。
进一步地，流量调节槽321a可以设为周向长度沿阀座芯321的轴向向下渐缩的结构，如图10中所示，该种结构可以使小流量范围的冷媒流量调节更加精准。当然，实际设置时，将流量调节槽321a设置为其他结构，如方形、圆形或椭圆形结构也是可行的，只是相较于前述结构，小流量范围内的调节精确度较低。
与螺母41连接的阀芯42设于阀腔内，具体地，位于所述第一腔体内，当阀芯42处于全关状态，关闭阀口30a时，阀芯42的侧壁能够封堵流量 调节槽321a，从而切断第一腔体和第二腔体的连通，当阀芯42在螺母41的带动下上移时，逐渐打开流量调节槽321a，并改变流量调节槽321a的流通面积，从而使第一腔体和第二腔体连通，并调节冷媒流量。显然，阀芯42和阀座芯321之间需要保持密封。
结合图3理解，具体的方案中，阀座芯321的芯腔设置为台阶孔，该台阶孔形成朝向上阀座31的台阶面，阀座芯321的上端插装有上限位套421，该上限位套421的上端具有环形的径向凸台，该径向凸台搭接于阀座芯321朝向上阀座31的上端面，如此，上限位套421的下端面即朝向阀口30a的端面、阀座芯12的内侧壁以及上述阀座芯321的台阶面形成安装槽，可在该安装槽内设置密封圈423。
进一步地，密封圈423和所述阀座芯321的台阶面之间还可以设置下限位套422。由于阀芯42通常设置为上小下大的结构，以确保对阀口30a的密封，为满足阀芯42的装配要求，阀座芯321的小径通孔与阀芯42之间存在装配间隙。下限位套422的设置可以避免由于装配间隙的存在，密封圈423在阀芯的往复运动中脱离所述安装槽。
更进一步地，密封圈423的外周面设置有助滑件423a，可将助滑件423a与密封圈423设为一体，即将助滑件423a包覆于密封圈423的外周，也可单独设置；当所述第一腔体和所述第二腔体存在压力差时，压力使密封圈423挤压变形，助滑件423a由于包覆在密封圈423的外周，能够方便地捕捉到密封圈423的挤压力，从而与阀芯42的外周壁贴合，保证密封性，同时助滑件423a的设置还可以减小阀芯42轴向移动时的摩擦阻力。
所述上限位套421还需与阀座芯321之间保持相对固定；该实施例中，可以在上阀座31的大径段的底部设置轴向凸部，形成朝向下阀座32的环形台阶面，上阀座31通过该轴向凸部插装于下阀座32，其环形台阶面与下阀座32的上端面贴合，且所述轴向凸部的下端将上限位套421压紧于阀座芯321的上端面；而且，上阀座31的该种结构设置也易于保证其与下阀座32的同轴度。当然，也可以通过其他方式固定上限位套421和阀座芯321，如焊接或螺纹连接等方式。
阀芯42处于全关状态时，还应确保其与阀口30a之间的密封性。
该实施例中，阀芯42的底端具有轴向凸出部，其上铆接有密封环425。当阀芯42处于全关状态时，密封环425的下端面与阀口30a贴合形成密封。显然，密封环425的外端直径大于阀口30a的直径。
进一步地，该直动式电动阀的电机10的转子12为永磁体转子，具体地可采用铷铁硼磁钢材料或各向异性铁氧体材料制作，如此，当阀芯42处于全关状态时，电机10断电，由于转子12为永磁体转子，电机10在断电状态下具有定位转矩，能够确保丝杆312和螺母41之间的相对位置，避免两者滑移，因此，在电机10断电的状态下，能够进一步确保阀芯42和阀口30a之间的密封性，避免内漏发生。
为了使电机10具有一定的定位转矩，转子12的外径与阀口30a的直径之比优选为0.8～1.8。
进一步地，阀芯42具有与所述容纳腔贯通的轴向通孔，螺母41的周壁具有通气槽41c，即阀芯42的平衡通道包所述容纳腔、与所述容纳腔贯通的轴向通孔以及设于螺母41周壁的通气槽41c；如此，阀芯42处于全关状态时，阀芯42上下端的压力平衡，可结合图3理解，图3示出了阀口全关状态下阀芯组件上下压力平衡的结构示意图。如图中箭头所示，第二接管323通过阀口30a与阀芯42的轴向通孔连通，并通过螺母41的通气槽41c连通上阀座31的大径腔31b，阀芯42受到的压差力较小，开启阀口30a时，仅需较小的驱动力即可，即用较小的电机10就可驱动较大的阀芯42，进一步将直动式电动阀小型化。
进一步地，阀芯42的轴向通孔的内壁下端开设有环形槽，其内设置有过滤网424；过滤网424的设置避免了冷媒流动时将杂质带入阀芯42的轴向通孔而导致丝杆312与螺母41配合的螺纹卡死。
另外，该直动式电动阀的上阀座31下腔的小径腔31a和大径腔31b连通处形成朝向阀口30a的台阶端面31c，该台阶端面31c和阀口30a之间的距离限定了阀芯42的轴向移动距离。如图1所示，当阀芯42处于全开状态时，流量调节槽321a全开，第一接管322通过流量调节槽321a与第二接管323连通，此时，阀芯42的上端面与台阶端面31c抵接；如图2所示，当阀芯42处于全闭状态时，其密封环425与阀口30a贴合形成密封， 第一接管322和第二接管323未连通，冷媒流通完全被切断。
该直动式电动阀能够实现双向流通，结合图1和图2理解，图1和图2中的箭头表明了冷媒的流向；其中，实线箭头表明冷媒从第一接管322流入，第二接管323流出，虚线箭头表明冷媒从第二接管323流入，第一接管322流出。
图15示出了装配直动式电动阀的流程示意图。所述直动式电动阀的装配方法包括如下步骤：
将组装好的阀芯组件400安装于组装好的下阀座组件302；
将组装好的上阀座组件301的丝杆312旋入阀芯组件400的螺母41，并将上阀座组件301的上阀座31与下阀座组件302的下阀座32焊接固定；
压装外壳20和固定架21，并组装电机10的线圈部件11。
其中，上阀座组件301的装配流程可参考图16，包括如下步骤：
压装丝杆312、轴承311和上阀座31；
安装垫片314于轴承311上端，将其与上阀座31铆接或焊接；
将衬套313卡设于丝杆312和垫片314之间，使其与轴承311的上端抵接，并与丝杆312焊接固定；
将电机10的转子12外套于上阀座31的上端，并与丝杆312固定连接。
阀芯组件400的装配流程可参考图17，包括如下步骤：
将密封环422和垫圈423铆接于阀芯42底端的轴向凸出部；
将螺母41的大径部41b压装于阀芯42的容纳腔；
将螺母盖板411与阀芯42焊接固定；
组装过滤网424和卡簧425。
本发明提供的直动式电动阀采用了上述直动式电动阀的装配方法，由于上述直动式电动阀具有上述技术效果，用于装配该直动式电动阀的装配方法也应具备相应的技术效果。这里不再赘述。
以上对本发明所提供的一种流量调节阀进行了详细介绍。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 (12)

  1. 一种直动式电动阀，包括具有阀腔的阀座(30)、设于所述阀座(30)上端的电机(10)以及丝杆(312)；所述丝杆(312)通过螺纹配合连接有螺母(41)，所述螺母(41)连接有阀芯(42)；其特征在于，所述电机(10)的转子(12)和所述阀座(30)的轴向位置相对固定，所述丝杆(312)的上端与所述转子(12)固定连接，所述阀芯(42)在所述螺母(41)的带动下能够沿所述阀腔轴向移动以开启或关闭设于所述阀座(30)上的阀口(30a)；所述阀芯(42)为具有平衡通道的筒状结构，且其外周设有将所述阀腔分隔为两个独立腔体的密封件。
  2. 如权利要求1所述的直动式电动阀，其特征在于，所述丝杆(312)通过环形连接片(315)与所述转子(12)焊接固定；所述环形连接片(315)的通孔周边沿轴向延伸形成突出部。
  3. 如权利要求1所述的直动式电动阀，其特征在于，所述转子(12)为永磁体转子；所述转子(12)的外径与所述阀口(30a)的直径之比为0.8～1.8。
  4. 如权利要求1所述的直动式电动阀，其特征在于，包括阀芯组件(400)、下阀座组件(302)和上阀座组件(301)，所述上阀座组件(301)包括上阀座(31)、丝杆(312)和电机(10)的转子(12)；所述上阀座(31)和所述下阀座组件(302)的下阀座(32)固定连接，且两者的内腔连通；所述转子(12)外套于所述上阀座(31)上端，并与所述上阀座(31)的轴向位置相对固定；所述丝杆(312)的上端穿过所述上阀座(31)与所述转子(12)固定连接，下端与所述阀芯组件(400)的螺母(41)螺纹配合，所述阀芯组件(400)的阀芯(42)在所述螺母(41)的带动下能够沿所述下阀座(32)的内腔轴向移动以开启或关闭设于所述下阀座(32)的阀口(32a)。
  5. 如权利要求4所述的直动式电动阀，其特征在于，所述上阀座(31)的内腔被环形板分隔为上腔(31c)和下腔，所述上腔(31c)内设置有轴承(311)，所述丝杆(312)通过所述轴承(311)与所述上阀座(31)的轴向位置相对固定。
  6. 如权利要求4或5所述的直动式电动阀，其特征在于，所述上阀座(31)外套有外壳(20)，所述电机(10)的线圈部件(11)外套于所述外壳(20)，并通过套设于所述外壳(20)的固定架(21)支撑；所述线圈部件(11)的轴向中心线、所述轴承(311)的轴向中心线以及所述转子(12)的轴向中心线重合。
  7. 如权利要求1至5任一项所述的直动式电动阀，其特征在于，所述螺母(41)包括与所述丝杆(312)螺纹配合的小径部(41a)和大径部(41b)；
    所述阀芯(42)的上端具有容纳所述螺母大径部(41b)的容纳腔，所述容纳腔的内壁上端开设有台阶面朝向所述转子(12)的环形台阶，其上设置螺母盖板(411)，以限制所述螺母(41)和所述阀芯(42)在轴向上的相对位置。
  8. 如权利要求7所述的直动式电动阀，其特征在于，所述阀芯(42)的平衡通道包括所述容纳腔、与所述容纳腔贯通的轴向通孔以及设于所述螺母(41)周壁的通气槽(41c)。
  9. 如权利要求8所述的直动式电动阀，其特征在于，所述轴向通孔的内壁下端开设有环形槽，其内设置有过滤网(424)。
  10. 如权利要求9所述的直动式电动阀，其特征在于，所述阀芯(42)的底端具有轴向凸出部，其上铆接有密封环(425)，所述阀芯(42)处于全关状态时，所述密封环(425)的下端面与所述阀口(30a)的端面贴合形成密封。
  11. 一种直动式电动阀的装配方法，其特征在于，包括如下步骤：
    将组装好的阀芯组件(400)安装于组装好的下阀座组件(302)；
    将组装好的上阀座组件(301)的丝杆(312)旋入所述阀芯组件(400)的螺母(41)，并将所述上阀座组件(301)的上阀座(31)与所述下阀座组件(302)的下阀座(32)焊接固定；
    压装外壳(20)和固定架(21)，并组装电机(10)的线圈部件(11)。
  12. 如权利要求11所述的装配方法，其特征在于，所述上阀座组件的装配包括如下步骤：
    压装丝杆(312)、轴承(311)和上阀座(31)；
    安装垫片(314)于所述轴承(311)上端，将其与所述上阀座(31)铆接或焊接；
    将衬套(313)卡设(301)于所述丝杆(312)和所述垫片(314)之间，使其与所述轴承(311)的上端抵接，并与丝杆(312)焊接固定；
    将电机(10)的转子(12)外套于所述上阀座(31)的上端，并与所述丝杆(312)固定连接。
PCT/CN2015/071065 2014-01-20 2015-01-20 一种直动式电动阀及其装配方法 Ceased WO2015106724A1 (zh)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113639048A (zh) * 2020-04-24 2021-11-12 浙江盾安禾田金属有限公司 电子膨胀阀及电子膨胀阀的制造方法

Families Citing this family (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2850254B2 (ja) 1989-09-27 1999-01-27 株式会社フジミインコーポレーテッド 研磨剤組成物
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
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
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
CN109723826B (zh) * 2017-10-27 2023-02-28 浙江三花商用制冷有限公司 一种电动阀
CN109780224A (zh) * 2017-11-13 2019-05-21 艾默生环境优化技术(苏州)有限公司 电子膨胀阀
WO2019148693A1 (zh) * 2018-01-31 2019-08-08 浙江三花制冷集团有限公司 一种电动阀及其制造方法
CN110296265A (zh) * 2018-03-23 2019-10-01 浙江三花智能控制股份有限公司 电子膨胀阀
CN110296266B (zh) * 2018-03-23 2021-08-27 浙江三花智能控制股份有限公司 电子膨胀阀
CN110296264B (zh) * 2018-03-23 2022-02-08 浙江三花智能控制股份有限公司 电子膨胀阀
JP7073925B2 (ja) * 2018-06-07 2022-05-24 株式会社デンソー 弁装置
EP3671070A1 (en) 2018-12-20 2020-06-24 Danfoss A/S Valve, in particular expansion valve
EP3671073A1 (en) 2018-12-20 2020-06-24 Danfoss A/S Electric expansion valve
CN111765251B (zh) * 2019-03-30 2023-08-01 浙江三花智能控制股份有限公司 电子膨胀阀
CN111765258B (zh) * 2019-04-02 2022-01-28 浙江三花制冷集团有限公司 一种电动阀
KR102718799B1 (ko) * 2019-06-04 2024-10-22 제지앙 둔안 아트피셜 인바이런먼트 컴퍼니 리미티드 파일럿 밸브 및 사방향 리버싱 밸브
CN112303266B (zh) * 2019-07-29 2024-01-30 浙江三花商用制冷有限公司 流量控制阀及其装配方法
CN112879576B (zh) * 2019-11-29 2023-01-06 杭州三花研究院有限公司 阀装置
CN111102360A (zh) * 2020-02-27 2020-05-05 黄晓峰 一种暖气阀
JP7141423B2 (ja) * 2020-04-09 2022-09-22 株式会社鷺宮製作所 電動弁および冷凍サイクルシステム
JP7034527B1 (ja) * 2020-07-10 2022-03-14 株式会社不二工機 電動弁
JP7113537B2 (ja) * 2020-09-04 2022-08-05 株式会社テージーケー 電動弁
CN114321396A (zh) * 2020-09-29 2022-04-12 浙江三花汽车零部件有限公司 电动阀
JP7161515B2 (ja) * 2020-11-30 2022-10-26 株式会社鷺宮製作所 電動弁及び冷凍サイクルシステム
CN112361671B (zh) * 2020-12-04 2024-12-10 上海众源燃油分配器制造有限公司 一种带有硬密封结构的电磁阀
CN114623240B (zh) * 2020-12-11 2023-03-14 浙江盾安人工环境股份有限公司 阀针组件及具有其的电子膨胀阀
CN114688270A (zh) * 2020-12-30 2022-07-01 浙江三花制冷集团有限公司 电动阀
EP4043768B1 (en) * 2021-02-15 2025-07-23 Goodrich Corporation Valve position detection
KR102359130B1 (ko) * 2021-05-04 2022-02-08 주식회사 삼양발브종합메이커 유량 제어 스마트 밸브와 이를 이용한 유량 제어 시스템
DE102021123957A1 (de) * 2021-09-16 2023-03-16 Hanon Systems Kältemittelventil
CN113819249A (zh) * 2021-09-29 2021-12-21 广东威灵电机制造有限公司 电子膨胀阀及制冷设备
CN114183207B (zh) * 2021-11-02 2023-11-28 中国长江动力集团有限公司 一种阀芯组件和可卸载调节阀

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006010004A (ja) * 2004-06-28 2006-01-12 Saginomiya Seisakusho Inc 電動式コントロールバルブ
JP2008267464A (ja) * 2007-04-18 2008-11-06 Fuji Koki Corp 電動弁
CN201916532U (zh) * 2011-01-06 2011-08-03 佛山市三俊电子股份有限公司 一种高精度数控恒温阀
JP2012013197A (ja) * 2010-07-05 2012-01-19 Fuji Koki Corp 電動弁
CN203223617U (zh) * 2013-02-28 2013-10-02 浙江盾安禾田金属有限公司 一种减速式电子膨胀阀

Family Cites Families (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE512667C (de) 1926-07-16 1930-11-15 Vormals Skodawerke Ag Elektromotorischer Antrieb fuer Hochdruck-Absperrventile
US4071041A (en) * 1976-01-07 1978-01-31 Acf Industries, Incorporated Ball valve seat ring construction
US4285498A (en) * 1976-05-17 1981-08-25 Imperial Chemical Industries Limited Control valves
US4473210A (en) * 1978-11-13 1984-09-25 Brighton John A Labyrinth trim valve
JPS62124378A (ja) 1985-11-19 1987-06-05 Mitsubishi Electric Corp 流量制御弁装置
US4705071A (en) * 1985-12-09 1987-11-10 Westinghouse Electric Corp. Steam control valve with improved muffler portion
JP2503930Y2 (ja) * 1990-03-15 1996-07-03 愛三工業株式会社 アイドル回転数制御装置
JP2000179731A (ja) 1998-12-15 2000-06-27 Saginomiya Seisakusho Inc 電動弁
JP3937029B2 (ja) 1999-03-26 2007-06-27 株式会社鷺宮製作所 電動弁
JP2001141097A (ja) * 1999-11-17 2001-05-25 Saginomiya Seisakusho Inc 電動流量制御弁
US6460567B1 (en) * 1999-11-24 2002-10-08 Hansen Technologies Corpporation Sealed motor driven valve
JP2001153236A (ja) * 1999-11-26 2001-06-08 Saginomiya Seisakusho Inc 二段式電動膨張弁
JP5060689B2 (ja) * 2001-04-13 2012-10-31 株式会社鷺宮製作所 流量制御弁及び流量制御弁の制御装置
US6536472B2 (en) * 2001-05-07 2003-03-25 Fisher Controls International, Inc. High performance fluid control valve
JP2003185302A (ja) 2001-10-10 2003-07-03 Fuji Koki Corp 電動弁
JP3978395B2 (ja) 2002-01-23 2007-09-19 愛三工業株式会社 流量制御弁
US7240694B2 (en) 2004-07-09 2007-07-10 Danfoss A/S Flow control valve for refrigeration system
JP4668160B2 (ja) * 2006-11-09 2011-04-13 株式会社森精機製作所 軸受ユニット及び該軸受ユニットを備えた工作機械の主軸装置
JP5725714B2 (ja) 2010-01-26 2015-05-27 株式会社不二工機 電動弁のコイルユニットの取付装置
WO2012045310A1 (en) * 2010-10-06 2012-04-12 Danfoss A/S A flow control valve and a method of assembling a flow control valve
JP5875777B2 (ja) * 2011-03-31 2016-03-02 株式会社不二工機 電動弁
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
JP5881367B2 (ja) 2011-10-19 2016-03-09 株式会社不二工機 パイロット式電動制御弁
CN103388939B (zh) 2012-05-11 2016-06-01 浙江三花股份有限公司 一种电子膨胀阀
CN203009981U (zh) 2012-12-25 2013-06-19 浙江三花股份有限公司 一种电子膨胀阀
CN203082326U (zh) 2013-01-10 2013-07-24 浙江盾安机械有限公司 一种蜗轮减速式电子膨胀阀

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006010004A (ja) * 2004-06-28 2006-01-12 Saginomiya Seisakusho Inc 電動式コントロールバルブ
JP2008267464A (ja) * 2007-04-18 2008-11-06 Fuji Koki Corp 電動弁
JP2012013197A (ja) * 2010-07-05 2012-01-19 Fuji Koki Corp 電動弁
CN201916532U (zh) * 2011-01-06 2011-08-03 佛山市三俊电子股份有限公司 一种高精度数控恒温阀
CN203223617U (zh) * 2013-02-28 2013-10-02 浙江盾安禾田金属有限公司 一种减速式电子膨胀阀

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3098494A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113639048A (zh) * 2020-04-24 2021-11-12 浙江盾安禾田金属有限公司 电子膨胀阀及电子膨胀阀的制造方法

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