WO2011044754A1 - 节流阀 - Google Patents

节流阀 Download PDF

Info

Publication number
WO2011044754A1
WO2011044754A1 PCT/CN2010/001593 CN2010001593W WO2011044754A1 WO 2011044754 A1 WO2011044754 A1 WO 2011044754A1 CN 2010001593 W CN2010001593 W CN 2010001593W WO 2011044754 A1 WO2011044754 A1 WO 2011044754A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
flow passage
plunger
coil
mounting hole
Prior art date
Application number
PCT/CN2010/001593
Other languages
English (en)
French (fr)
Inventor
金仁召
Original Assignee
宁波奥柯汽车空调有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 宁波奥柯汽车空调有限公司 filed Critical 宁波奥柯汽车空调有限公司
Priority to BRPI1006046A priority Critical patent/BRPI1006046A2/pt
Priority to JP2011537835A priority patent/JP5281694B2/ja
Priority to US13/143,177 priority patent/US9010724B2/en
Publication of WO2011044754A1 publication Critical patent/WO2011044754A1/zh

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F25B41/345—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
    • F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
    • F16K3/26—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members with fluid passages in the valve member
    • F16K3/267—Combination of a sliding valve and a lift valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0668—Sliding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the invention relates to a throttle valve for regulating flow, which is particularly suitable for use in an inverter air conditioner, a commercial air conditioner, a central air conditioner, a refrigerated food display cabinet, and a constant temperature and humidity device.
  • Throttle valves in refrigeration systems can generally be divided into capillary throttling, thermal expansion valve throttling (internal balancing, external balancing), and electronic expansion valve throttling.
  • the electronic expansion valve is a new type of throttling device, which is controlled by a microprocessor. Its appearance realizes direct control and adjustment of the refrigeration cycle of the microcomputer.
  • the electronic expansion valve is characterized by a large adjustment range. The action is quick and sensitive, the adjustment is precise, stable and reliable, and the refrigerant can flow in both positive and negative directions in the electronic expansion valve, avoiding the disadvantage that the thermal expansion valve has only one direction, and the refrigeration system can be greatly simplified when used for the heat pump.
  • the electronic expansion valve can be completely closed, so that there is no need to install a solenoid valve at the refrigerant inlet, so the electric expansion valve is favored by the refrigeration industry.
  • the electronic expansion valve we usually refer to is a split motor type, which is composed of a valve body, a valve core, a bellows, a transmission mechanism, and a pulse stepping machine.
  • the pulse stepping motor is a driving mechanism, a bellows.
  • the refrigerant is separated from the moving parts to prevent the refrigerant from leaking.
  • the function of the transmission mechanism is to convert the rotary motion of the motor into the reciprocating motion of the valve core to determine the opening degree of the valve port, thereby controlling the flow rate of the refrigerant. .
  • the above electronic expansion valve structure is basically similar.
  • the gear mechanism has no gear pair.
  • the sub-expansion valve is costly.
  • a throttle valve includes a valve body having a mouth and an outlet on a wall of the valve body, and a valve body communicating with the inlet and the outlet in the valve body, the valve The body also has a mounting hole penetrating through the flow channel; the valve core is inserted into the mounting hole and can slide relative to the wide body, and the outer peripheral wall of the valve core and the inner wall of the mounting hole are fluid-tightly fitted, and the spool is The outer end protrudes out of the valve body, the inner end of the valve core enters the flow passage, and the cleaning of the valve core can change the flow cross section of the flow passage to regulate the flow of the fluid through the flow passage; the spool drive structure is disposed outside the valve body The valve core connection of the valve body is exposed; the valve core driving structure directly drives the axial sliding of the valve core, the valve core driving structure comprises a valve seat, is fixed on the valve body, and has a concave cavity in the valve seat, The
  • the mounting hole penetrates the flow passage;
  • the valve core is a plunger, and the middle portion of the plunger has an annular groove, and the annular groove matches the flow passage, and the area of the annular groove and the cross section of the flow passage is determined.
  • a flow cross section of the flow passage an upper portion of the plunger is located in the mounting hole above the flow passage, and a balance hole is formed in the upper wall of the mounting hole above the flow passage; a lower portion of the plunger is located in the mounting hole below the flow passage;
  • the outer end of the plunger enters the cavity, and the bottom surface of the cavity is provided with a vent hole.
  • the venting hole may also be an exhausting gap, which mainly ensures smoother downward movement of the plunger, which is a specific valve core structure, and the valve core structure of the plunger is particularly suitable for a horizontal flow path in a shape of a line. .
  • a sealing ring seal is arranged between the upper peripheral wall of the plunger and the inner peripheral wall of the mounting hole, and a sealing ring is provided between the lower peripheral wall of the plunger and the inner peripheral wall of the mounting hole. seal.
  • the sealing method of the sealing ring has the advantages of simple structure and convenient installation.
  • the valve body is an alloy die-casting part, so its wear resistance is poor. If the plunger directly rubs against the inner wall of the valve body mounting hole, it is easy to wear the wide body, resulting in the liquid between the plunger and the mounting hole. The sealing property is reduced.
  • the above-mentioned mounting hole is tightly embedded with a liner, and the peripheral wall of the liner is provided with a through hole communicating with the flow passage, the through hole is located in the flow passage, and the cross section of the flow passage The through hole is completely penetrated, and the plunger is located inside the liner.
  • the liner can be made of a wear-resistant material such as wear-resistant steel, so that the plunger does not directly rub against the inner wall of the mounting hole, but directly rubs against the inner wall of the liner, and the liner is not easily worn. Therefore, the service life of the throttle valve can be greatly improved.
  • a seal seal is provided between the upper outer peripheral wall of the plunger and the inner peripheral wall of the liner, and a seal ring seal is provided between the lower outer peripheral wall of the plunger and the inner peripheral wall of the liner.
  • the upper part of the iron core is connected to the lower end of the plunger through the connecting piece, which is convenient for connecting the iron core to the plunger.
  • the iron core can also be directly fixed to the plunger, and the lower part of the iron core is directly fixed with the magnetic element.
  • the elastic member may be a spring yellow, and the elastic body II is located in a mounting hole above the flow path and supported at the upper end of the plunger
  • the bomb can also be located in the mounting hole below the runner and supported on the lower end of the plunger.
  • a coiled sleeve is embedded in the coil described above > the magnetic element is located within the sleeve.
  • the above elastic member may also be a disc.
  • the disc is like two.
  • the cavity of the valve seat is provided with an upper support sleeve and a lower support sleeve.
  • the coil is limited to the upper support sleeve and the lower support.
  • the two disc springs are respectively located above and below the coil, wherein the periphery of one disc spring is pressed between the upper support sleeve and the upper end surface of the coil, the center of the disc spring is fixed with the iron core, and the other disc is like The periphery is pressed between the lower support sleeve and the lower end of the coil, the center of the disc. Fixed with the iron core.
  • the flow passage is L-shaped, the valve core is a valve needle, the tapered head of the valve needle is matched with the lower jaw of the vertical portion of the flow passage, and the outer end of the valve needle 6b enters the concave cavity 2i.
  • the bottom surface of the cavity 21 is provided with a vent hole 22.
  • the venting hole can also be an venting gap, which mainly ensures that the valve needle moves downwards more smoothly, which is another relatively conventional valve core structure.
  • the above elastic member is a bullet.
  • the bullet is sleeved on the valve needle, the upper end of the spring is in contact with the lower end surface of the valve body, and the lower end of the spring abuts against the annular shoulder at the lower end of the valve needle.
  • the mounting method of the bullet is suitable for the case where the spool is a valve needle.
  • the advantage of the present invention is that the spool driving mode of the throttle valve is different from the prior art, and the electromagnetic driving of the spool is axially slipped, which eliminates the existing expansion enthalpy.
  • the stepping motor, gear pair and thread pair structure in the spool drive structure are simple in structure, low in cost and light in weight, and the throttle valve involves fewer components, so the wear between the components is less, and also because of this section.
  • the spool in the drive structure of the flow valve has only one translational action to ensure smooth operation of the throttle valve.
  • Figure 1 is a schematic view showing the structure of the first embodiment of the present invention (the maximum flow cross section of the flow path);
  • Figure 2 is a schematic view showing the structure of the first embodiment of the present invention (the flowing flow cross section is in an intermediate state);
  • Figures 3 to 5 are schematic views of the plunger structure in the first embodiment of the present invention (the annular groove has different cross-sectional shapes;
  • Figure 6 is a schematic view showing the structure of the second embodiment of the present invention (the maximum flow state of the flow path):
  • Figure 7 is a schematic view showing the structure of the second embodiment of the present invention (the flow cross section of the flow path is in an intermediate state);
  • Figure 8 is a schematic view of the structure of the first embodiment of the present invention (the maximum flow cross section of the flow path);
  • Figure 9 is a schematic view showing the structure of a third embodiment of the present invention (the flow cross section of the flow path is in an intermediate state);
  • Figure 10 is a schematic view showing the structure of the fourth embodiment of the present invention (the maximum flow state of the flow path);
  • Figure U is a schematic view of the structure of the fourth embodiment of the present invention (the flow cross section of the flow passage is in an intermediate state);
  • Figure 12 is a schematic view showing the structure of the fifth embodiment of the present invention (the maximum flow state of the flow passage);
  • Figure 13 is a schematic view showing the structure of a fifth embodiment of the present invention (the flow cross section of the flow path is in an intermediate state);
  • Figure 14 is a structural diagram of the sixth embodiment of the present invention (the maximum flow state of the flow path);
  • Figure 15 is a schematic view showing the structure of a sixth embodiment of the present invention (the flow cross section of the flow path is in an intermediate state);
  • Fig. 6 is a schematic view showing the structure of the seventh embodiment of the present invention (the flow cross section of the flow path is in an intermediate state).
  • Valve body the wall of the valve body is provided with an inlet 11 and an outlet 1.2.
  • the port 11 and the outlet 12 are located on the same horizontal axis, and the valve body has a flow passage D connecting the inlet 11 and the outlet 12, and the flow passage 13
  • the axis of the valve body is a straight line.
  • the valve body I also has a mounting hole 14 extending through the flow channel 13.
  • the mounting hole 14 extends through the flow channel 13. In this embodiment, the mounting hole and the two ends are crossed.
  • the valve core, the valve core in this embodiment is a plunger 6a, which is inserted into the mounting hole 14 and can slide downward relative to the valve body 1.
  • the upper portion of the plunger 6a is located in the flow passage 13-... t
  • a sealing ring 15 is sealed between the upper outer peripheral wall of the plunger 6a and the inner peripheral wall of the mounting hole 14, and a balance hole 141 is formed in the top wall of the mounting hole 14 above the flow channel;
  • the lower portion of the 6a is located in the ampoule hole 14 below the flow path 23, and a seal ring 15 is sealed between the outer peripheral wall of the F portion of the plunger 6a and the inner peripheral wall of the mounting hole 14, thereby preventing fluid (such as refrigerant) from being sealed.
  • the two ends of the plunger 6a are leaked; the middle portion of the plunger 6a has an annular groove 6al.
  • the cross-section of the annular I-groove 6al in this embodiment has a concave arc shape, and may be other shapes such as a front-reverse conical shape or a pointed needle shape, such as As shown in FIGS.
  • the annular groove 6a1 is matched with the flow path 13, and the area of the annular groove 6al and the cross-section of the flow path 13 determines the flow cross section of the flow path 13, and when the annular groove 6al is completely located in the flow path 13, , the fluid (such as refrigerant) through the 1 ⁇ 2 flow rate is large, when the annular groove 6al is all located in the flow In the case of the road, the flow passage 13 is cut off, and the fluid (such as refrigerant) cannot pass through the flow passage, that is, the larger the area of the annular groove 6al and the flow passage 13 is, the larger the flow rate of the fluid (such as the refrigerant) through the flow passage is. Therefore, the axial slip of the plunger 6a can change the flow cross section of the flow passage 13 to regulate the flow rate of the fluid through the flow passage 13.
  • the outer end of the plunger 6a protrudes outside the valve body 1.
  • the spool driving structure is disposed outside the valve body 1 and connected to the plunger 6a of the externally exposed valve body, and the spool driving structure directly drives the plunger 6a to axially slide.
  • the spool drive structure includes
  • the valve seat 2 is fixed to the lower part of the valve body 2 by a screw gun.
  • the valve seat has a cavity 2 1 .
  • the outer end of the plunger 6 a extends out of the valve body 1 and enters the cavity 21 .
  • the bottom surface of the cavity 21 is provided with exhaust gas. Hole 22 ;
  • the coil 3 is mounted in the cavity 21 of the valve seat, and a wire bushing 3 is embedded in the wire country 3, and two connecting wires 32 on the coil pass through the bottom of the valve seat 2 to lead out of the valve seat 2, Thus, the connecting wire 32 can be connected to the power source.
  • the cylindrical magnetic element 4 made of a magnetic material is placed in the cylindrical guide bush 3 1 , and the inner circumference of the guide bush 31 is bonded to the outer peripheral surface of the magnetic element 4 to guide The outer peripheral surface of the sliding sleeve 3 1 is bonded to the inner peripheral surface of the coil 3, and the magnetic element 4 is driven by the electromagnetic force generated by the coil 3 to be electrically moved and slipped relative to the coil 3.
  • the iron core 5 is connected to the plunger 6a and the magnetic member 4.
  • the upper portion of the iron core 5 is connected to the lower end of the plunger 6a via the engaging member 10, and the lower portion of the iron core 5 is directly fixed to the magnetic member 4.
  • the elastic member, the elastic member in this embodiment is a bullet II 8a, and the elastic 8a is located in the mounting hole 14 above the flow channel and
  • the generated electromagnetic electromagnetic force is greater than the spring force of the spring spring 88aa, and the electromagnetic electromagnetic The magnetic force pushes the movable magnetic magnetic element component 44 and the iron core core 55 to slide upward upward, and then the belt plunger 61aa is slid upward and upward, and is in the column.
  • the plug 66aa When the plug 66aa is moved up and down, the gas body in the mounting hole MM located above the flow channel is discharged from the horizontal balance hole 114411, and at the same time, The upper upper edge of the ring-shaped concave groove groove 66aall is moved upward with respect to the convection flow path 1133, and the lower half of the column plunger plug 66aa is opened and begins to cover the flow path.
  • the cross-sectional plane of 1133 is such that the flow volume of the fluid flow body (e.g., such as a refrigerant refrigerant) flowing through the inlet port 1111 is reduced less by the flow rate through the flow channel port 33.
  • the column plunger plug produces a raw resistance damping force which gradually increases and increases gradually, when used as an effect on the electromagnetism force on the column plunger plug 66aa and the resistance of the spring spring 88aa.
  • the damping force reaches the balance balance, the column plunger plug 66aa is kept at a certain position, and reaches the adjustable throttle body (for example, cooling and cooling) The agent)) passes through the amount of flow through the enthalpy. .
  • the inlet port 1111 flows through.
  • the refrigerant refrigerant can not flow out from the outlet port 1122 through the overflow passage. .
  • the column plunger plug 66aa When the electromagnetism force acting as the action on the magnetic magnetic element member 44 is smaller than the spring force of the spring spring 88aa.., the column plunger plug 66aa is elastic at the spring of the projectile 88aa. The action of the force is started to slide down and down, and the gas gas in the concave cavity 22 of the valve seat is discharged from the exhaust gas hole 2222, and at the same time, The upper edge of the ring-shaped concave groove groove 66aall is moved downward relative to the convection channel 1133, and the lower half of the column plunger plug 66aa begins to gradually move away from the open channel.
  • the cross-sectional plane of 1133 causes the flow volume of the fluid body (such as a refrigerant refrigerant) flowing through the inlet port 1111 to gradually increase by the flow rate iitt 1133.
  • the bomb 11 88aa gradually recovers and restores its original shape, and the resistance force of the resistance to the column plunger plug 66aa is gradually reduced and reduced, and is used as a function.
  • the electromagnetism force on the column plunger plug 66aa and the resistance of the cartridge 88aa When the damping force is reached again to reach the balance balance, the column plunger plug 66aa is kept at a certain position, and reaches the reverse reverse adjustment section.
  • the fluid body (such as, for example, a refrigerant refrigerant) passes through the purpose of the flow rate of the passing fluid. .
  • the embodiment example and the first embodiment of the first embodiment are different from each other in that the inner mounting hole 1144 is tightly fitted with a liner tube.
  • the tube 99, the circumferential wall of the liner tube 99 is arranged 11:::: opening, there is a through hole 9911 communicating with the flow port 1133,
  • the through hole 99 is located in the flow channel 1133, and the cross-sectional surface of the flow channel 1133 is completely penetrated through the through hole 99!!
  • the column plunger 66aa is located In the inner liner of the lining pipe;; the outer upper peripheral peripheral wall of the column plunger plug 66aa and the inner peripheral wall of the liner pipe 99 are provided with a tight seal ring]] 55
  • a tight seal is provided, and a seal seal ring 1155 is tightly sealed between the lower outer peripheral outer peripheral wall of the column plunger plug 66aa and the inner peripheral wall of the liner pipe 99. .
  • the lining pipe can be made of a material with good wear resistance and wear resistance, such as wear-resistant steel, so that the plunger plug will not And the inner wall of the mounting hole of the installation and the hole is directly connected with the friction rubbing, but the inner peripheral wall of the inner liner of the liner pipe is directly connected to the friction rub, and the liner is lined.
  • the tube is not easy to be easily worn and worn, and therefore, this can greatly improve the life expectancy of the valve of the throttle valve. . - As shown in Figures 88 and 99, the third and third examples of the implementation of the new and new types are practical examples. .
  • the embodiment example and the first embodiment of the first embodiment are different from each other in that the elastic member is a spring magazine 88aa.
  • the spring spring 88aa is located in the concave cavity 2211 on the valve seat, and the support beam is on the lower end surface of the magnetic magnetic element member 44. .
  • the direction of the coil of the coil of the current coil should be opposite to that of the first embodiment, that is, even if the coil of the coil is paired with the magnetic magnetic component Produce a living electromagnetic electromagnetic force
  • the mounting hole 14 is tightly embedded with a liner 9 having a through hole 91 communicating with the flow passage 13 on the peripheral wall of the liner 9, and the through hole 9 is located in the flow.
  • the cross section of the flow passage 13 completely penetrates the through hole 91, and the plunger 6a is located in the liner 9.
  • the upper peripheral wall of the plunger 6a and the inner peripheral wall of the liner 9 are sealed with a sealing ring 15
  • a seal ring 15 is sealed between the lower outer peripheral wall of the plunger 6a and the inner peripheral wall of the liner 9.
  • the elastic member is a disc 8b
  • the disc has two
  • the cavity 21 of the valve seat is provided with a h support sleeve ⁇ 6 and a lower support sleeve.
  • the coil 3 is limited between the upper support sleeve 16 and the lower support sleeve 17, two discs are respectively located under the coil 3 ...
  • one of the discs 8 8 is pressed around the upper support sleeve Between the cylinder 16 and the upper end surface of the coil 3, the center of the disc 8b is fixed to the core 5 located at the upper portion of the magnetic member 4, and the periphery of the other disc 8b is pressed against the lower support sleeve 1 and the end of the coil 3' ⁇ F The center of the disc 8b is fixed to the core 5 located at the lower portion of the magnetic member 4.
  • a liner 9 is tightly embedded in the mounting hole M.
  • the peripheral wall of the liner 9 is provided with a through hole 91 communicating with the flow raft 13, and the through hole 91 is located in the flow passage 1. 3, and the cross section of the flow passage 13 completely penetrates the through hole 91, the plunger 6a is located in the liner 9; the upper peripheral wall of the plunger 6ii and the inner peripheral wall of the liner 9 are provided with a sealing ring 15 sealed, the plunger 6a A sealing ring 15 is sealed between the lower outer peripheral wall and the inner peripheral wall of the liner 9. As shown in Fig. 16, this is a seventh embodiment of the present invention.
  • This embodiment differs from the first embodiment in that the flow passage 13 in the valve body is L-shaped, the valve body is the valve needle 6b, the tapered head portion 6b l of the valve needle 6b and the lower portion of the straight portion of the flow passage 13
  • the mouth is matched, that is, the slip of the valve needle b can change the opening size of the lower opening of the vertical portion of the flow channel to adjust the flow rate of the fluid through the flow passage 13, the outer peripheral wall of the 'F portion of the valve needle 6b and the inner peripheral wall of the mounting hole 14.
  • a seal ring 15 is provided between the seals 15 and the outer end of the valve needle 6b enters the cavity 21, and the bottom surface of the I.I cavity 2 1 is provided with a vent hole 22,
  • the elastic member is a spring 8a, and the spring 8a is sleeved on the valve needle 6b.
  • the L end of the spring 8a is in contact with the lower end surface of the valve body 1, and the lower end of the spring a abuts against the annular shoulder of the valve needle 6b F end.
  • the aforementioned magazine 8a is located in the cavity 21 on the valve seat and supported on the lower end surface of the magnetic member 4. At this time, the direction in which the coil 3 is energized should be opposite to that of the first embodiment, even if the electromagnetic force generated by the coil 3 on the magnetic member 4 is opposite to that of the first embodiment, the electromagnetic force of the magnetic member 4 is directed downward.
  • the opening degree of the lower opening of the vertical portion of the flow passage 13 gradually becomes smaller; as the valve needle 6b moves up, the flow rate of the fluid (e.g., refrigerant) decreases, and as the spring 8a is compressed, the damping force generated to the valve needle 6b Gradually, when the electromagnetic force acting on the valve needle 6b is balanced with the spring force of the spring 8a, the valve needle 6b is held at a certain position S for the purpose of regulating the flow rate of the fluid (e.g., refrigerant).
  • the fluid e.g., refrigerant
  • the tapered head 6b.l of the needle 6b When moving, the tapered head 6b.l of the needle 6b gradually moves away from the 'F opening of the vertical portion of the flow passage 13, and the opening of the lower opening of the vertical portion of the flow raft 13 gradually becomes larger; with the valve needle 6b Moving downward, the flow rate of the fluid (such as refrigerant) increases, the spring 8a gradually returns to its original shape, and the damping force generated to the valve needle 6b gradually decreases, and the electromagnetic force acting on the valve needle 6b and the spring force of the spring 8a again reach When balancing, the valve needle 6b is held in a position to achieve the reverse adjustment of the fluid (such as refrigerant)
  • the fluid such as refrigerant

Landscapes

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

Description

一种节流阀
技术领域
本发明涉及一种调节流量的节流阀， 其特别适用用于变频空调、商用空调、 中央空 调、 冷藏食品陈列柜及恒温恒湿等设备。 背景技术
制冷系统中的节流阀通常可以分为毛细管节流， 热力膨胀阀节流 (内平衡、 外平衡) 和电子膨胀阀节流。 前， 在制冷系统中， 电子膨胀阀是一种新型的节流装置， 它由微 处理器进行控制， 它的出现实现了微机直接控制和调节制冷循环， 电子膨胀阀的特点是 调节范围大、 动作迅速灵.敏、 调节精密、 稳定可靠， 制冷剂在电子膨胀阀中可以正、 逆 两个方向流动， 避免了热力膨胀阀只有一个方向的缺点， 用于热泵时可使制冷系统大为 简化， 制冷系统停机时， 电子膨胀阀可以完全关闭， 使制冷剂进口处无需安装电磁阀， 因此电于膨胀阀备受制冷行业的宵睐„
目前我们所说的电子膨胀阀通常指的是歩进电机型， 它由阀体、 阀芯、 波纹管、 传 动机构和脉冲步进¾机等组成， 脉冲步进电机是驱动机构， 波纹管是将制冷剂通遒与运 动部件隔开， 以防制冷剂泄露， 传动机构的作用是将电机的旋转运动转变为阀芯的往复 运动， 以决定阀口的开启程度， 从而控制制冷剂的流量。 关于电子膨胀阀的专利文献也 有很多， 如一专利号为 ZL02266124.7 (公吿号为 CN2564804Y)的中国实用新型专利《变 频空调电子膨胀阀》 披露的膨胀阀结构， 又如 ··· ·专利号为 ZL02261051 .0 (公吿号为 CN2580367Y)的中 I 实用新型专利《变频空调用直动式电子膨胀阀》披露的膨胀阀结构， 还如 ·· ·'专利号为 ZL20042()()23433.0 (公吿号为 CN2703169Y)的中国实用新型专利《变频 空调用减速式电子膨胀阀》 披露的膨胀阀結构。
以上电子膨胀阀结构基本类似，将电机的旋转运动转变为阀芯的往复运动传动机构 有两种， 一种是减速式传动机构包括齿轮副、 螺纹副、 传动杆等， 另- 种是直动式传动 机构没有齿轮副。 前述无论哪种传动机构， 涉及部件多， 存在结构而且复杂重量重的缺 陷； 再有其一般需要有歩进电机作为动力源， 众所周知， 歩进电机价格昂贵， 因此现有 调节制冷剂流量的 ¾子膨胀阀成本高.。
综―..匕所述， 现有调节流量的节流阀还可作进一歩改进。 发明内容
1
更正页（细则第 91条) 本发明所要解决的技术问题是针对上述现有技术现状而提供一种结构新颖简单而 且成本低的节流阀， 该节流阀还具有各构件之间磨损少动作平稳的优点》
本发明解决上述技术问题所采用的技术方案为： 一种节流阀， 包括有阀体， 阀体的 壁上开有迸口和出口， 阀体内具有连通所述进口和出口的流遒， 阀体上内还具有与所述 流道贯通的安装孔； 阀芯， 活动插设在安装孔内并能相对阔体滑移， 阀芯外周壁与安装 孔内壁之间液密封配合， 阀芯的外端伸出阀体外， 阀芯的内端进入所述流道， 阀芯的清 移能改变流道的流动截面以调节流体通过流道的流量； 阀芯驱动结构， 设于阀体外部 外露出阀体的阀芯连接； 其特征在于： 所述阀芯驱动结构直接驱动阀芯轴向滑移， 该阀 芯驱动结构包括阀座， 固定在阀体上， 阀座内具有凹腔， 所述阀芯伸出阀体后进入该凹 腔内， 凹腔底面设有排气孔； 线圈， 安装在阀座的凹腔内； 磁性元件， 位于线圈内， 该 磁性元件在线圈通电后产生电磁力的作用下被驱动而相对线圈滑移； 铁芯， 连接所述阀 芯和磁性元件； 弹性件， 作用于所述阀芯， 该弹性件对阀芯产生的阻尼力相抗于线圈对 磁性元件产生的电磁力。
上述的安装孔贯穿所述流道； 所述的阀芯为柱塞， 该柱塞的中部具有环形凹槽， 该 环形凹槽与流道相配， 环形凹槽与流道截面重合面积的多少决定流道的流动截面； 柱塞 的上部位于在流道上方的安装孔内， 在流道上方的安装孔上项壁上开有平衡孔； 柱塞的 下部位于在流道下方的安装孔内； 柱塞的外端进入所述凹腔内， 凹腔底面设有排气孔。 该排气孔也可以是一种排气间隙，主要保证柱塞下移更为顺畅， 其为一种具体的阀芯结 构， 柱塞的阀芯结构特别适合用于呈一字形的水平流道。
为确保柱塞与安装孔之间的密封，上述的柱塞的上部外周壁与安装孔内周壁之间设 有密封圈密封， 柱塞的下部外周壁与安装孔内周壁之间设有密封圈密封。釆用密封圈的 密封方式具有结构简单， 安装方便的优点。
- ·般阀体为合金压铸件， 故其耐磨性较差，如果柱塞直接与阀体安装孔的内壁进行 摩擦滑移， 很易磨损阔体， 导致柱塞与安装孔之间的液密封性降低， 作为改进， 上述的 安装孔内紧嵌有一衬管, 该衬管周壁上开有与所述的流道连通的通孔， 所述的通孔位于 流道内， 且流道的截面完全贯穿该通孔， 所述的柱塞位于衬管内。 这样衬管可以采用耐 磨性好的材料如耐磨性钢材制成， 这样柱塞不会和安装孔的内壁直接摩擦， 而是与衬管 内壁直接靡擦， 而衬管又不易被磨损， 因此能大大提高该节流阀的使用寿命。
为确保柱塞与衬管之间的密封，上述的柱塞的上部外周壁与衬管内周壁之间设有密 封圈密封， 柱塞的下部外周壁与衬管内周壁之间设有密封圈密封。 采用密封圈的密封方 式具有结构简单， 安装方便的优点。
上述的铁芯上部通过衔接件与柱塞下端连接，该方式便于将铁芯与柱塞连接， 当然 铁芯也可直接与柱塞固定， 铁芯下部与磁性元件直接固定。
上述的弹性件可以为弹黃， 该弹 II位于流道上方的安装孔内并支撑在柱塞的上端
2
更正页（细则第 91条) 面； 弹费还可以位于流道下方的安装孔内并支撑在柱塞的下端面。
为防止线圈被磁性元件在滑移过程中磨损，上述的线圈内嵌设有一导滑套筒>所述 的磁性元件位于该套筒内。
上述的弹性件还可为碟贊，该碟赞有二片，所述阀座的凹腔内设有上支撑套筒和下 支撑套筒， 所述的线圈限位于上支撑套筒和下支撑套筒之间， 所述两片碟簧分别位于线 圈上下方， 其中一片碟簧的周边被压制在上支撑套筒和线圈上端面之间， 碟簧的中心与 铁芯固定， 另一片碟赞的周边被压制在下支櫞套简和线圈下端面之间， 碟黉的中心.与铁 芯固定》 '
上述的流道呈 L 形， 所述的阀芯为阀针， 阀针的锥形头部与流道竖直部分的下部 幵口相配， 阀针 6b的外端进入所述凹腔 2i内， 凹腔 21底面设有排气孔 22。 该排气孔 也可以是一种排气间隙，主要保证阀针下移更为顺畅，其为另 -种较为常规的阀芯结构。
上述的弹性件为弹赞， 该弹赞套设在阀针上， 弹簧的上端与阀体下端面抵触， 弹簧 的下端抵靠在阀针下端的环形挡肩上。 该弹贊的安装方式适合用于阀芯为阀针的情况。
现有技术相比，本发明的优点在于：本节流阀的阀芯驱动方式与现有技术不相同， 其为电磁方式驱动阀芯轴向滑移， 该驱动方式省却了现有膨胀闽中阀芯驱动结构中的步 进电机、 齿轮副及螺纹副结构， 因此结构简单、 成本低、 重量轻， 而且本节流阀涉及部 件少， 故构件之间的磨损也就少， 还因为本节流阀的驱动结构中的阀芯只有一个平移动 作， 确保节流阀动作的平稳。 附图说明
图 1为本发明第 - 个实施例的结构示意图 (流道的流动截面最大状态)；
图 2为本发明第 -〜个实施例的结构示意图 (流遒的流动截面处于中间状态)； 图 3〜5为本发明第一个实施例中柱塞结构示意图 (环形凹槽不同截面形状； 图 6为本发明第二个实施例的结构示意图 (流道的流动截面最大状态)：
图 7为本发明第二个实施例的结构示意图 (流道的流动截面处于中间状态)； 图 8为本发明第王个实施例的结构不意图 (流道的流动截面最大状态)；
图 9为本发明第三个实施例的结构示意图 (流道的流动截面处于中间状态)； 图 10为本发明第四个实施例的结构示意图 (流道的流动截面最大状态)；
图 U.为本发明第四个实施例的结构示意图 (流道的流动截面处于中间状态)； 图 12为本发明第五个实施例的结构示意图 (流通的流动截面最大状态)；
图 13为本发明第五个实施例的结构示意图 (流道的流动截面处于中间状态)； 图 14为本发明第六个实施例的结构示窻图 (流道的流动截面最大状态)；
图 15为本发明第六个实施例的结构示意图 (流道的流动截面处于中间状态)； 图】6为本发明第七个实施例的结构示意图 (流道的流动截面处于中间状态)。
3
更正页（细则第 91条) 具体实施方式
以下结合附图实施例对本发明作进一步详细描述。
如簡 1〜5所示， 为本发明的第一个实施例。
•种节流阀， 包括有
阀体】， 阀体的壁上开有进口 11和出口 1.2 , 该迸口 1 1和出口 12位于同一水平轴 线上， 阀体〗 内具有连通进口 11和出口 12的流道 D , 流道 13的轴线为直线， 阀体 I 上内还具有与流道 13贯通的安装孔 14， 安装孔 14贯穿所述流道 13， 本实施例中安装 孔与两端呈十字交叉。
阀芯， 本实施例中的阀芯为柱塞 6a, 活动插设在安装孔 14内并能相对阀体 1轴向 上下滑移， 柱塞 6a的上部位于在流道 13―... t方的安装孔 1.4内， 柱塞 6a的上部外周壁与 安装孔 14内周壁之间设有密封圈 1 5密封， 在流道上方的安装孔 14的顶壁上开有平衡 孔 141 ; 柱塞 6a的下部位于在流道 23下方的安鈹孔 .14内， 柱塞 6a的 F部外周壁与安 装孔 14内周壁之间设有密封圈 15密封，这样能防止流体 (如制冷剂)从柱塞 6a两端泄露； 柱塞 6a的中部具有环形凹槽 6al， 本实施例中的环形 I槽 6al的截面成凹弧状， 也可以 是正反圆锥面状或尖针状等其它形状， 如图 3〜5所示， 环形凹槽 6al与流道 13相配， 环形凹槽 6al与流道 13截面重合面积的多少决定流道 13的流动截面， 当环形凹槽 6al 正好全部位于流道 13内， 流体 (如制冷剂)通过 ½流量大， 当环形凹槽 6al全部位于流道 夕卜， 则流道 13被截断， 流体 (如制冷剂)不能通过流道， 即环形凹槽 6al与流道 13截面 重合面积越大， 流体 (如制冷剂） 通过流道的流量越大， 故柱塞 6a的轴向滑移能改变流 道 13的流动截面以调节流体通过流遒 13.的流量； 柱塞 6a的外端伸出阀体 1外。
阀芯驱动结构， 设于阀体 1外部与外露出阀体〗的柱塞 6a连接， 阀芯驱动结构直 接驱动柱塞 6a轴向滑移。
阀芯驱动结构包括
阀座 2， 通过螺枪固定在阀体 2下部， 阀座内具有凹腔 2 1， 柱塞 6a的外端伸出阀 体 1后进入该凹腔 21内， 凹腔 21底面设有排气孔 22 ;
线圈 3 , 安装在阀座的凹腔 21 内， 线國 3内嵌设有-一导滑套筒 3 1， 线圈上的两根 连接导线 32穿过阀座 2底部而引出阀座 2外， 这样连接导线 32便能与电源接通。
由磁性材料制成的呈圆筒状的磁性元件 4， 位于虽圆筒状的导滑套筒 3 1 内， 导滑 套筒 31.的内周丽与磁性元件 4的外周面贴合， 导滑套筒 3 1的外周面与线圈 3的内周面 贴合， 该磁性元件 4在线圈 3通电后产生电磁力的作用下被驱动而相对线圈 3滑移。
铁芯 5，连接柱塞 6a和磁性元件 4，铁芯 5上部通过衔接件 10与柱塞 6a下端连接， 铁芯 5下部与磁性元件 4直接固定。
弹性件， 本实施例中的弹性件为弹 II 8a, 弹赞 8a位于流道上方的安装孔 14内并
4
更正页（细则第 91条) 支支撑撑在在柱柱塞塞 66aa的的上上端端面面，， 该该弹弹簧簧 88aa作作用用于于柱柱塞塞 66aa，， 该该弹弹簧簧 88aa对对柱柱塞塞 66aa产产生生的的阻阻尼尼力力 相相抗抗于于线线圈圈、、对对磁磁性性元元件件 44产产生生的的电电磁磁力力，， 使使柱柱塞塞 在在移移动动过过程程中中保保持持稳稳定定。。
由由于于电电磁磁感感应应原原理理，， 当当线线圈圈 33通通电电后后产产生生的的电电磁磁力力大大于于弹弹簧簧 88aa的的弹弹力力时时，， 电电磁磁力力 推推动动磁磁性性元元件件 44及及铁铁芯芯 55向向上上滑滑动动，， 进进而而带带动动柱柱塞塞 66aa向向上上滑滑动动，， 在在柱柱塞塞 66aa上上移移时时，， 位位 于于流流道道上上方方的的安安装装孔孔 MM内内气气体体从从平平衡衡孔孔 114411排排出出，， 同同时时，， 环环形形凹凹槽槽 66aall 上上缘缘相相对对流流道道 1133上上移移，， 柱柱塞塞 66aa下下半半部部杆杆径径开开始始逐逐歩歩遮遮住住流流道道 1133的的截截面面，， 使使进进口口 1111流流过过来来的的流流体体 ((如如 制制冷冷剂剂))经经流流道道 ΪΪ 33的的流流量量减减少少，， 随随着着弹弹蟹蟹 88aa被被压压缩缩，， 对对柱柱塞塞 产产生生的的阻阻尼尼力力逐逐渐渐增增大大，， 当当作作用用在在柱柱塞塞 66aa上上的的电电磁磁力力与与弹弹簧簧 88aa的的阻阻尼尼力力达达到到平平衡衡时时，， 柱柱塞塞 66aa保保持持在在某某个个位位置置 上上，， 达达到到调调节节流流体体 ((如如制制冷冷剂剂))通通过过的的流流量量的的罔罔的的。。
如如果果环环形形凹凹槽槽 66aall下下部部的的柱柱塞塞周周面面完完全全遮遮蔽蔽住住流流道道 1133时时，，进进口口 1111流流过过来来的的制制冷冷剂剂 不不能能通通过过流流道道从从出出口口 1122流流出出。。
当当作作用用于于磁磁性性元元件件 44的的电电磁磁力力小小于于弹弹簧簧 88aa..的的弹弹力力时时，， 柱柱塞塞 66aa在在弹弹獰獰 88aa弹弹力力作作用用 下下开开始始下下滑滑，， 位位于于阀阀座座的的凹凹腔腔 22 ]]内内气气体体从从排排气气孔孔 2222排排出出，， 同同时时，， 环环形形凹凹槽槽 66aall上上缘缘相相 对对流流道道 1133下下移移，， 柱柱塞塞 66aa下下半半部部杆杆径径开开始始逐逐步步离离开开流流道道 1133的的截截面面，， 使使进进口口 1111流流过过来来的的 流流体体 ((如如制制冷冷剂剂))经经流流 iitt 1133的的流流量量逐逐渐渐增增大大，， 弹弹 11 88aa逐逐渐渐恢恢复复原原状状，， 对对柱柱塞塞 66aa产产生生的的阻阻 尼尼力力逐逐渐渐减减小小，， 当当作作用用在在柱柱塞塞 66aa上上的的电电磁磁力力与与弹弹黉黉 88aa的的阻阻尼尼力力再再一一次次达达到到平平衡衡时时，， 柱柱 塞塞 66aa保保持持在在某某个个位位置置上上，， 达达到到反反向向调调节节流流体体 ((如如制制冷冷剂剂))通通过过的的流流量量的的目目的的。。
' ' 如如果果环环形形凹凹槽槽 66aa::ll下下部部的的柱柱塞塞周周面面完完全全离离开开住住流流道道 11 33，， 环环形形凹凹槽槽 66aa ii 正正好好全全部部位位 于于流流道道 ..11 33内内时时，， 进进 JJ ]]流流过过来来的的制制冷冷剂剂以以最最大大的的流流量量通通过过流流道道，， 从从出出口口 1122流流出出。。 如如图图 66、、 77所所示示，， 为为本本实实用用新新型型的的第第二二个个实实施施例例。。
该该实实施施例例和和第第一一个个实实施施例例的的不不同同点点在在于于，， 安安装装孔孔 1144 内内紧紧嵌嵌有有一一衬衬管管 99，， 该该衬衬管管 99 周周壁壁 ..........11::：：开开有有与与流流遒遒 1133连连通通的的通通孔孔 9911，，通通孔孔 99 11位位于于流流道道 1133内内，， 且且流流道道 1133的的截截面面完完全全贯贯 穿穿该该通通孔孔 99 !!，， 柱柱塞塞 66aa位位于于衬衬管管 内内；； 柱柱塞塞 66aa的的上上部部外外周周壁壁与与衬衬管管 99内内周周壁壁之之间间设设有有密密 封封圈圈 ]] 55密密封封，， 柱柱塞塞 66aa的的下下部部外外周周壁壁与与衬衬管管 99内内周周壁壁之之间间设设有有密密封封圈圈 1155密密封封。。
衬衬管管可可以以采采用用耐耐磨磨性性好好的的材材料料如如耐耐磨磨性性钢钢材材制制成成，，这这样样柱柱塞塞不不会会和和安安装装孔孔的的内内壁壁直直 ''接接摩摩擦擦，， 而而是是^^衬衬管管内内周周壁壁直直接接摩摩擦擦，， 而而衬衬管管又又不不易易被被磨磨损损，， 因因此此能能大大大大提提高高该该节节流流阀阀 的的使使用用寿寿命命。。 ―― 如如图图 88、、 99所所示示，， 为为本本实实用用新新型型的的第第三三个个实实施施例例。。
该该实实施施例例和和第第一一个个实实施施例例的的不不同同点点在在于于，， 弹弹性性件件虽虽然然也也为为弹弹黉黉 88aa,, 该该弹弹簧簧 88aa位位于于 阀阀座座上上的的凹凹腔腔 2211 内内并并支支樑樑在在磁磁性性元元件件 44的的下下端端面面。。
这这时时线线圈圈通通电电的的方方向向应应该该与与第第一一个个实实施施例例相相反反，， 即即使使线线圈圈对对磁磁性性元元件件产产生生的的电电磁磁力力
Figure imgf000007_0001
更正页（细则第 91条) 如图 10、 l i所示， 为本实用新型的第四个实施例。
该实施例和第三个实施例的不同点在于， 安装孔 14 内紧嵌有 -衬管 9, 该衬管 9 周壁上开有与流道 13连通的通孔 91 ,通孔 9】位于流道】.3内，且流道 13的截面完全贯 穿该通孔 91， 柱塞 6a位于衬管 9内； 柱塞 6a的上部外周壁与衬管 9内周壁之间设有密 封圈 15密封， 柱塞 6a的下部外周壁与衬管 9内周壁之间设有密封圈 15密封。 如图】 2、 13所示， 为本实用新型的第五个实施例。
本实施例和第三个实施例的不同点在于： 其弹性件为碟赞 8b， 该碟赞 b有二片， 阀座的凹腔 21内设有 h支撑套筒 ί 6和下支撑套筒 17， 线圈 3限位于上支撑套筒 16和 下支撺套筒 17之间， 两片碟赞 分别位于线圈 3 ...1:：下方， 其中一片碟赞 8b的周边被 压制在上支撑套筒 16和线圈 3上端面之间， 碟贊 8b的中心与位于磁性元件 4上部的铁 芯 5固定，另 - 片碟赞 8b的周边被压制在下支撑套筒 1 和线圈 3 '· F端面之间，碟篑 8b 的中心与位于磁性元件 4下部的铁芯 5固定。
当磁性元件 4带动柱塞 6a滑移时， 碟簧 8b就会变形对柱塞 6a起阻尼作用。 如图 14、 1 5所示， 为本实用新型的第六个实施例。
该实施例和第五个实施例的不同点在于， 安装孔 M 内紧嵌有一衬管 9， 该衬管 9 周壁上开有与流遒 13连通的通孔 91，通孔 91位于流道 1 3内，且流道 13的截面完全贯 穿该通孔 91 , 柱塞 6a位于衬管 9内； 柱塞 6ii的上部外周壁与衬管 9内周壁之间设有密 封圈 15密封， 柱塞 6a的下部外周壁与衬管 9内周壁之间设有密封圈 1 5密封。 如图 16所示， 为本实用新型的第七个实施例。
该实施例和第一个实施例的不同点在于，阀体内的流道 13呈 L形， 阀芯为阀针 6b， 阀针 6b的锥形头部 6b l与流道 13坚直部分的下部幵口相配， 即阀针 b的滑移能改变 流道 Π竖直部分的下部开口的开启大小以调节流体通过流道 13的流量， 阀针 6b的' F 部外周壁与安装孔 14内周壁之间设有密封圈 15密封， 阀针 6b的外端进入所述凹腔 21 内， I. I腔 2 1底面设有排气孔 22 ,,
弹性件为弹簧 8a， 该弹簧 8a套设在阀针 6b上， 弹簧 8a的 ..... L端与阀体 1下端面抵 触， 弹 a的下端抵靠在阀针 6b F端的环形挡肩 6b2上。
当然前述弹赘 8a位于阀座上的凹腔 21内并支撑在磁性元件 4的下端面。这时线圈 3通电的方向应该与第一个实施例相反， 即使线圈 3对磁性元件 4产生的电磁力与第一 个实施例相反， 磁性元件 4受到的电磁力朝下。
由于电磁感应原理， 当线圈 3通电后产生的电磁力大于弹箫 8a的弹力时， 电磁力
6
更正页（细则第 91条) 推动磁性元件 4及铁芯 5向上滑动， 进而带动阀针 6b向上滑动， 在阀针 6b上移时， 阀 针 6b的锥形头部 6bl逐渐伸入流道 3竖直部分的下部幵口， 流道 13竖直部分的下部 开口的开启度逐渐变小； 随着阀针 6b上移， 流体 (如制冷剂)通过的流量减少， 随着弹簧 8a被压缩， 对阀针 6b产生的阻尼力逐渐增大， 当作用在阀针 6b上的电磁力与弹簧 8a 的弹力达到平衡时， 阀针 6b保持在某个位 S上， 达到调节流体 (如制冷剂；)通过的流量的 目的。
如果， 阀针 6b的锥形头部 6b I 完全插入流道 13竖直部分的下部开口内， 迸。 11 流过来的制冷剂不能通过流道从出口 12流出， 锥形头部 6bl越离开下部开口， 制冷剂 通过流道的流量越大。
当作用于磁性元件 4的电磁力小于弹簧 8a的弹力时， 阀针 6b在弹簧 8a弹力作用 下幵始下滑， 位于阀座的凹腔 2〖内气体从排气孔 22排出 , 在隱 6b下移时 , 闹针 6b 的锥形头部 6b.l逐渐远离流道 13竖直部分的 ' F部开口， 流遛 13竖直部分的下部开口的 幵启度逐渐变大； 随着阀针 6b下移， 流体 (如制冷剂)通过的流量增加， 弹簧 8a逐渐恢 复原状， 对阀针 6b产生的阻尼力逐渐减小， 当作用在阀针 6b上的电磁力与弹簧 8a的 弹力再一次达到平衡时， 阀针 6b保持在某个位置上， 达到反向调节流体 (如制冷剂)通过
更正页（细则第 91条)

Claims

权 利 要 求
• 1、 一种节流阔， 包括有
阀体 (1)， 阀体的壁上开有进口（11)和出口（12)， 阔体 (1)内具有连通所述进口和出口 的流道 (13)， 阀体 (1)内还具有与所述流道 (13)贯通的安装孔 (14);
阀芯， 活动插设在安装孔 (14)内并能相对阀体 (1)滑移， 阀芯外周壁与安装孔内壁之 间液密封配合， 阀芯的外端伸出阀体 (1)外， 阀芯的内端进入所述流道 (13)， 阀芯的滑移 能改变流道 (13)的流动截面以调节流体通过流道 (13)的流量；
阀芯驱动结构， 设于阔体 (1)外部与外露出阀体 (1)的阀芯连接；
其特征在于： 所述阀芯驱动结构直接驱动阀芯轴向滑移， 该阀芯驱动结构包括 阔座 (2)， 固定在阀体 (1)上， 阀座内具有凹腔 (21)， 所述阀芯伸出阀体 (1)后进入该 凹腔 (21)内；
线圈 (3)， 安装在阀座的凹腔 (21)内；
磁性元件 (4)， 位于线圈 (3)内， 该磁性元件 (4)在线圈 (3)通电后产生电磁力的作用下 被驱动而相对线圈 (3)滑移；
铁芯 (5)， 连接所述阀芯和磁性元件 (4);
弹性件， 作用于所述阔芯， 该弹性件对阀芯产生的阻尼力相抗于线圈 (3)对磁性元 件 (4)产生的电磁力。
2、 根据权利要求 1 所述的节流阀， 其特征在于： 所述的安装孔 (14)贯穿所述流道 (13)； 所述的阀芯为柱塞 (6a)， 该柱塞 (6a)的中部具有环形凹槽 (6al)， 该环形凹槽 (6al) 与流道 (13)相配， 环形凹槽 (6al)与流道 (13)截面重合面积的多少决定流道 (13)的流动截 面； 柱塞 (6a)的上部位于在流道 (13)上方的安装孔 (14)内， 在流道上方的安装孔 (14)上顶 壁上开有平衡孔 (141); 柱塞 (6a)的下部位于在流道 (23)下方的安装孔 (14)内； 柱塞 (6a)的 外端进入所述凹腔 (21)内， 凹腔 (21)底面设有排气孔 (22)。
3、 根据权利要求 2所述的节流阀， 其特征在于： 所述的柱塞 （6a)的上部外周壁与 安装孔 (14)内周壁之间设有密封圈 (15)密封， 柱塞 (6a)的下部外周壁与安装孔 (14)内周壁 之间设有密封圈 (15)密封。
4、 根据权利要求 2所述的节流阀， 其特征在于： 所述的安装孔 (14)内紧嵌有一衬 管 (9)， 该衬管 (9)周壁上开有与所述的流道 (13)连通的通孔 (91)， 所述的通孔 (91)位于流 道 (13)内， 且流道 (13)的截面完全贯穿该通孔 (91)， 所述的柱塞 (6a)位于衬管 (9)内。
5、 根据权利要求 4所述的节流阔， 其特征在于： 所述的柱塞 (6a)的上部外周壁与 衬管 (9)内周壁之间设有密封圈 (15)密封， 柱塞 (6a)的下部外周壁与衬管 (9)内周壁之间设 有密封圈 (15)密封。
6、根据权利要求 2所述的节流阀，其特征在于：所述的铁芯 (5)上部通过衔接件 (10) 与柱塞 (6a)下端连接， 铁芯 (5)下部与磁性元件 (4)直接固定。
7、 根据权利要求 2所述的节流阀， 其特征在于： 所述的弹性件为弹簧 (8a)， 该弹 簧 (8a)位于流道上方的安装孔 (14)内并支撑在柱塞 (6a)的上端面。
8、 根据权利要求 2所述的节流阀， 其特征在于： 所述的弹性件为弹簧 (8a)， 该弹 簧 (8a)位于阀座上的凹腔 (21)内并支撑在磁性元件 (4)的下端面。
9、 根据权利要求 7或 8所述的节流阀， 其特征在于： 所述的线圈 (3)内嵌设有一导 滑套筒 (31)， 所述的磁性元件 (4)位于该套筒 (31)内。
10、 根据权利要求 2所述的节流阀， 其特征在于： 所述的弹性件为碟簧 (8b)， 该碟 簧 (8b)有二片， 所述阀座的凹腔 (21)内设有上支撑套筒 (16)和下支撑套筒 (17)， 所述的线 圈 (3)限位于上支撑套筒 (16)和下支撑套筒 (17)之间， 所述两片碟簧 (8b)分别位于线圈 (3) 上下方， 其中一片碟簧 (8b)的周边被压制在上支撑套筒 (16)和线圈 (3)上端面之间， 碟簧 (8b)的中心与铁芯 (5)固定， 另一片碟簧 (8b)的周边被压制在下支撑套筒 (17)和线圈 (3)下 端面之间， 碟簧 (8b)的中心与铁芯 (5)固定。
11、 根据权利要求 1所述的节流阀， 其特征在于： 所述的流道 (13)呈 L形， 所述的 阀芯为阀针 (6b)，阀针 (6b)的锥形头部 (6bl)与流道 (13)竖直部分的下部开口相配，阀针 (6b) 的外端进入所述凹腔 (21)内， 凹腔 (21)底面设有排气孔 (22)。
12、 根据权利要求 11 所述的节流阀， 其特征在于： 所述的弹性件为弹簧 (8a)， 该 弹簧 (8a)套设在阀针 (6b)上， 弹簧 (8a)的上端与阔体 (1)下端面抵触， 弹簧 (8a)的下端抵靠 在阀针 (6b)下端的环形挡肩 (6b2)上。
PCT/CN2010/001593 2009-10-13 2010-10-12 节流阀 WO2011044754A1 (zh)

Priority Applications (3)

Application Number Priority Date Filing Date Title
BRPI1006046A BRPI1006046A2 (pt) 2009-10-13 2010-10-12 válvula borboleta
JP2011537835A JP5281694B2 (ja) 2009-10-13 2010-10-12 スロットルバルブ
US13/143,177 US9010724B2 (en) 2009-10-13 2010-10-12 Throttle valve

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN200910206816.9 2009-10-13
CN2009102068169A CN101691890B (zh) 2009-10-13 2009-10-13 一种节流阀

Publications (1)

Publication Number Publication Date
WO2011044754A1 true WO2011044754A1 (zh) 2011-04-21

Family

ID=42080598

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2010/001593 WO2011044754A1 (zh) 2009-10-13 2010-10-12 节流阀

Country Status (6)

Country Link
US (1) US9010724B2 (zh)
JP (1) JP5281694B2 (zh)
KR (1) KR101602257B1 (zh)
CN (1) CN101691890B (zh)
BR (1) BRPI1006046A2 (zh)
WO (1) WO2011044754A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9010724B2 (en) 2009-10-13 2015-04-21 Ningbo Allko Automobile Air-Conditioners Co., Ltd. Throttle valve

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011196428A (ja) * 2010-03-18 2011-10-06 Fuji Electric Co Ltd 電子膨張弁
CN102606793B (zh) * 2012-03-26 2013-06-19 宁波奥柯汽车空调有限公司 一种电磁膨胀阀
DE102013204640A1 (de) * 2013-03-15 2014-09-18 Ti Automotive Technology Center Gmbh Ventil
JP6272247B2 (ja) * 2015-02-02 2018-01-31 株式会社鷺宮製作所 絞り装置及び冷凍サイクル
KR101557755B1 (ko) * 2015-03-27 2015-10-06 주식회사 경동나비엔 자동 밸브의 체결구조 및 그 자동 밸브를 이용한 온수 매트
US10852752B2 (en) * 2018-02-26 2020-12-01 Hitachi Metals, Ltd. High flow low pressure control valve
CN110220002A (zh) * 2019-06-19 2019-09-10 宁波兴茂电子科技有限公司 一种节能电磁阀
CN111365911B (zh) * 2020-03-23 2021-10-29 浙江农林大学暨阳学院 一种膨胀阀及汽车空调系统
CN112892082B (zh) * 2021-02-26 2024-04-05 成都市倍诚分析技术有限公司 一种涡流制冷排液阀
CN114593260A (zh) * 2022-02-28 2022-06-07 浙江三花智能控制股份有限公司 一种电磁阀装置

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5232195A (en) * 1991-03-08 1993-08-03 Fiat Auto S.P.A. Flow regulating valve
CN2312387Y (zh) * 1997-06-11 1999-03-31 威海市道通实业联合公司 一种电磁阀
JPH11118058A (ja) * 1997-10-16 1999-04-30 Koganei Corp 電磁弁ソレノイド
US5984261A (en) * 1996-11-20 1999-11-16 Aisin Seiki Kabushiki Kaisha Flow control valve unit including electric coil actuated rod
CN2524028Y (zh) * 2002-01-19 2002-12-04 刘亚军 电磁开关阀
US6837478B1 (en) * 1999-11-16 2005-01-04 Continental Teves Ag & Co., Ohg Electromagnet valve
CN2713230Y (zh) * 2004-05-19 2005-07-27 浙江三花股份有限公司 新型常开直流电磁阀
CN2783060Y (zh) * 2005-03-30 2006-05-24 浙江三花股份有限公司 节流、低噪音常开电磁阀
CN101691890A (zh) * 2009-10-13 2010-04-07 金仁召 一种节流阀
CN201517624U (zh) * 2009-10-13 2010-06-30 金仁召 一种节流阀
CN201599419U (zh) * 2009-10-13 2010-10-06 金仁召 一种节流阀

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2601549A (en) * 1947-01-02 1952-06-24 Admiral Corp Restricting valve
US3625474A (en) * 1969-11-21 1971-12-07 Julius R Juede Solenoid-actuated high-temperature fluid valves
US3670768A (en) * 1970-06-08 1972-06-20 Dynak Inc Fluid flow control device
JPS5940670U (ja) * 1982-09-10 1984-03-15 株式会社ボッシュオートモーティブ　システム 比例制御弁装置
US4635683A (en) * 1985-10-03 1987-01-13 Ford Motor Company Variable force solenoid
JPH0238778A (ja) * 1988-07-28 1990-02-08 Toyota Autom Loom Works Ltd 冷却回路における電磁膨張弁
DE9402205U1 (de) * 1994-02-10 1994-04-28 Hydraulik Ring Gmbh Proportionalmagnet-Ventileinheit
JP3424861B2 (ja) * 1994-10-06 2003-07-07 株式会社鷺宮製作所 ステップ流量制御弁
KR0127551B1 (ko) * 1995-09-19 1998-04-06 배순훈 앤티로크 브레이크 시스템용 솔레노이드 밸브 및 제조방법
JPH11202947A (ja) * 1998-01-09 1999-07-30 Sumitomo Electric Ind Ltd 電磁比例圧力制御弁の駆動制御方法
JP2003139261A (ja) * 2001-08-23 2003-05-14 Denso Corp 電磁弁装置および電磁弁装置の製造方法
JP4306519B2 (ja) * 2003-09-29 2009-08-05 アイシン・エィ・ダブリュ株式会社 圧力制御弁
US8047222B2 (en) * 2004-10-18 2011-11-01 Wilden Pump And Engineering Llc Air valve for an air driven reciprocating device
US20060097211A1 (en) * 2004-11-10 2006-05-11 Spurlock Michael S Air intake control device for a paint gun
US7367636B2 (en) * 2005-02-16 2008-05-06 Bendix Commercial Vehicle Systems, Llc Solenoid armature with integrated spherical soft seal
US8167000B2 (en) * 2007-04-05 2012-05-01 Mac Valves, Inc. Balanced solenoid valve
WO2009005149A1 (ja) * 2007-07-04 2009-01-08 Eagle Industry Co., Ltd. ソレノイドバルブ
JP2009203991A (ja) * 2008-02-26 2009-09-10 Jtekt Corp 電磁弁
CN102016374B (zh) * 2008-08-29 2014-03-19 伊格尔工业股份有限公司 电磁阀

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5232195A (en) * 1991-03-08 1993-08-03 Fiat Auto S.P.A. Flow regulating valve
US5984261A (en) * 1996-11-20 1999-11-16 Aisin Seiki Kabushiki Kaisha Flow control valve unit including electric coil actuated rod
CN2312387Y (zh) * 1997-06-11 1999-03-31 威海市道通实业联合公司 一种电磁阀
JPH11118058A (ja) * 1997-10-16 1999-04-30 Koganei Corp 電磁弁ソレノイド
US6837478B1 (en) * 1999-11-16 2005-01-04 Continental Teves Ag & Co., Ohg Electromagnet valve
CN2524028Y (zh) * 2002-01-19 2002-12-04 刘亚军 电磁开关阀
CN2713230Y (zh) * 2004-05-19 2005-07-27 浙江三花股份有限公司 新型常开直流电磁阀
CN2783060Y (zh) * 2005-03-30 2006-05-24 浙江三花股份有限公司 节流、低噪音常开电磁阀
CN101691890A (zh) * 2009-10-13 2010-04-07 金仁召 一种节流阀
CN201517624U (zh) * 2009-10-13 2010-06-30 金仁召 一种节流阀
CN201599419U (zh) * 2009-10-13 2010-10-06 金仁召 一种节流阀

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9010724B2 (en) 2009-10-13 2015-04-21 Ningbo Allko Automobile Air-Conditioners Co., Ltd. Throttle valve

Also Published As

Publication number Publication date
US20110297858A1 (en) 2011-12-08
CN101691890B (zh) 2011-08-31
CN101691890A (zh) 2010-04-07
JP5281694B2 (ja) 2013-09-04
BRPI1006046A2 (pt) 2016-05-10
KR101602257B1 (ko) 2016-03-10
JP2012510033A (ja) 2012-04-26
KR20120064056A (ko) 2012-06-18
US9010724B2 (en) 2015-04-21

Similar Documents

Publication Publication Date Title
WO2011044754A1 (zh) 节流阀
KR101342780B1 (ko) 파일럿형 제어 밸브
EP3620728A1 (en) Motor operated valve
JP4570484B2 (ja) 複合弁およびヒートポンプ式空気調和装置およびその制御方法
EP3418613A1 (en) Electric valve
JP2008064301A (ja) パイロット型制御弁
CN201599419U (zh) 一种节流阀
WO2020259656A1 (zh) 一种电子膨胀阀
CN113188275A (zh) 一种可防螺纹卡死的电子膨胀阀
CN111102366A (zh) 电子膨胀阀
JP7105721B2 (ja) 電動弁及び冷凍サイクルシステム
CN109506033A (zh) 一种先导式电磁阀
KR101609384B1 (ko) 가변 용량 압축기용 전자제어밸브
CN201517624U (zh) 一种节流阀
CN214949953U (zh) 一种可防螺纹卡死的电子膨胀阀
CN216715238U (zh) 一种燃气调节阀、阀体总成及燃气灶
CN101298954A (zh) 内置感温控制元件的膨胀阀
CN112413149B (zh) 电子膨胀阀及其安装方法
CN112879573A (zh) 一种电子膨胀阀
JP7453091B2 (ja) 電動弁および冷凍サイクルシステム
CN217784258U (zh) 电子膨胀阀组件、电子膨胀阀及制冷设备
CN209012499U (zh) 电子膨胀阀及使用该电子膨胀阀的空调系统
WO2022206164A1 (zh) 一种电动阀
WO2022166782A1 (zh) 一种电动阀
JPH01155164A (ja) 制御弁

Legal Events

Date Code Title Description
ENP Entry into the national phase

Ref document number: 20117011287

Country of ref document: KR

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 2011537835

Country of ref document: JP

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 10822986

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 1287/MUMNP/2011

Country of ref document: IN

WWE Wipo information: entry into national phase

Ref document number: 13143177

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 10822986

Country of ref document: EP

Kind code of ref document: A1

REG Reference to national code

Ref country code: BR

Ref legal event code: B01A

Ref document number: PI1006046

Country of ref document: BR

ENP Entry into the national phase

Ref document number: PI1006046

Country of ref document: BR

Kind code of ref document: A2

Effective date: 20110629