WO2012065437A1 - 一种膨胀阀 - Google Patents
一种膨胀阀 Download PDFInfo
- Publication number
- WO2012065437A1 WO2012065437A1 PCT/CN2011/075928 CN2011075928W WO2012065437A1 WO 2012065437 A1 WO2012065437 A1 WO 2012065437A1 CN 2011075928 W CN2011075928 W CN 2011075928W WO 2012065437 A1 WO2012065437 A1 WO 2012065437A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve
- hole
- expansion valve
- opening
- spool
- Prior art date
Links
Classifications
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- 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
- F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
- F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
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- 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
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
- F16K31/1221—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston one side of the piston being spring-loaded
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/06—Details of flow restrictors or expansion valves
- F25B2341/064—Superheater expansion valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/06—Details of flow restrictors or expansion valves
- F25B2341/068—Expansion valves combined with a sensor
Definitions
- the present invention relates to the field of refrigeration technology, and in particular, to an expansion valve.
- an expansion valve In the refrigeration cycle system loop, an expansion valve is usually installed.
- the expansion valve controls the opening degree of the valve by the superheat of the evaporator outlet or the compressor suction section in the induction refrigeration system, thereby realizing system refrigerant flow regulation and throttling.
- the role of pressure is usually installed.
- Figure 1 is a schematic view of a typical expansion valve structure.
- the expansion valve typically has an inlet tube 900 and an outlet tube 400 from which high pressure fluid from the condenser enters, throttling and depressurizing and flowing from the outlet tube 400 to the evaporator.
- the upper end of the expansion valve includes a gas box head 100 and a transmission rod 200.
- the transmission rod 200 is connected to the valve core 500.
- the valve seat 1000 is located at the intersection of the outlet tube 400 and the inlet tube 900.
- the valve core 500 is engaged with the valve seat 1000, and the valve core 500 is passed.
- the spring 600 abuts against the support member 700.
- the bottom of the support member 700 is connected to the adjustment rod 800.
- the valve body 500, the support member 700 and the spring 600 are located in the valve housing, and the adjustment rod 800 is fixed to the adjustment seat.
- a temperature sensing package is arranged at the outlet of the evaporator, the temperature sensing package senses the outlet temperature of the evaporator, the temperature is too high, and the working medium pressure in the temperature sensing package increases, and the diaphragm passes through the capillary to the diaphragm head to make it downward. Movement, driving the transmission rod 200 to push the valve core 500 away from the valve seat 1000, the spool 500 can control the size of the connection opening between the inlet tube 900 and the outlet tube 400 by the pressure generated by the temperature sensing package.
- the high pressure condensing pressure generates a force for opening the valve core 500 through the inlet pipe 900
- the evaporation pressure from the outlet pipe 400 generates a force for closing the valve body 500 in the closing direction, and therefore, the spool 500 is not only subjected to the valve.
- the force generated by the spool 500 due to the high and low pressure differentials is additionally tolerated.
- the high and low pressure differentials against the spool 500 The influence of the system is small, but for large-capacity valves or high-pressure refrigeration systems, the high and low pressure differentials have a great influence on the system of the force of the spool 500, so that the superheat of the expansion valve does not reflect the true superheat of the evaporator. Greatly reduce the efficiency of the system. Moreover, if such a structural expansion valve is used in a system requiring a bidirectional operation such as a heat pump, the high and low pressure differentials generated during cooling and heating are completely reversed to the force generated by the spool 500, so that the two directions cannot be static. The same degree of superheat will make the working efficiency of one of the cycles of cooling or heating more obvious.
- the structure of the spool 500 has been modified in the prior art, and a through hole is formed in the spool 500, and the pressure from the inlet tube 900 can be balanced by the inner and outer end faces of the spool 500.
- a structural expansion valve is forced by the valve core 500 to achieve a force balance, the performance is not stable enough, and the valve core 500 has a complicated structure, a large weight, a large amount of consumables, and also increases the load of the adjustment spring 600;
- the connection between the rod 800 and the support member 700 is complicated, and processing and assembly are troublesome.
- the technical problem to be solved by the present invention is to provide an expansion valve which has a function of more stably balancing the influence of high and low pressure difference on the spool.
- the present invention provides an expansion valve including a valve body having a chamber, a valve seat located in the chamber, and a valve body, a first opening and a second opening communicating with the chamber, The spool is moved relative to the valve seat to control a size of a flow path between the first opening and the second opening, the spool including a spool head facing the valve seat, The spool head is provided with an axial through hole, and the axial through hole is provided with a piston, and the piston is connected to the valve body.
- the axial through hole is an equal diameter hole connected to an end surface of the spool head.
- the axial through hole includes a small diameter hole connected to an end surface of the valve core head and a large diameter hole connected to the small diameter hole to form a step, and the piston is disposed in the large diameter hole.
- the axial cross-sectional area has a minimum cross-sectional area that is more than 0.6 times the maximum flow area at the valve port of the valve seat.
- the minimum cross-sectional area of the axial through hole is the maximum flow at the valve port of the valve seat More than 0.9 times the area.
- the valve core head is connected with a base portion, the base portion has an inner cavity, and the base portion is provided with a balance hole that communicates the inner cavity and the second opening.
- a sealing member is disposed between the hole wall of the axial through hole and the piston.
- the piston is dry connected to the support member of the spool by a piston connection 4.
- the adjusting rod of the expansion valve is provided with a first external thread
- an inner wall of the adjusting seat of the expansion valve is provided with a first internal thread adapted to the first external thread.
- the bottom of the support member has a bottom groove into which the upper end of the adjustment rod is press-fitted.
- the bottom of the support member has a recess adapted to the top end of the adjustment rod.
- the top of the support member has a top recess for the lower end of the piston connecting rod to be press fitted.
- the valve head of the expansion valve provided by the invention has an axial through hole, and a piston is arranged in the axial through hole, and the piston is connected with the valve body, and the fluid pressure acting on the valve core is mainly received by the piston. Since the piston is connected to the valve body, the pressure is finally transmitted to the valve body, which is balanced by the valve body. Therefore, the pressure of the fluid does not affect the working performance of the spool, and the opening of the spool can more accurately reflect the change in the superheat of the evaporator outlet.
- the expansion valve uses the valve body itself to balance the force, and can more stably balance the influence of the high and low pressure difference on the spool.
- Figure 1 is a schematic view of a typical expansion valve structure
- FIG. 2 is a schematic structural view of a specific embodiment of an expansion valve provided by the present invention.
- Figure 3 is a cross-sectional view taken along line A-A of Figure 2;
- Figure 4 is an axial sectional view of the expansion valve spool shown in Figure 3;
- Figure 5 is a perspective view showing the structure of the valve body shown in Figure 4.
- Figure 6 is a schematic structural view of another embodiment of the expansion valve according to the present invention
- Figure 7 is an axial sectional view of the valve core shown in Figure 6;
- Figure 8 is an axial cross-sectional view of the support member of the expansion valve shown in Figure 2;
- FIG. 10 is a schematic structural view of still another embodiment of an expansion valve according to the present invention.
- the core of the present invention is to provide an expansion valve which has a function of more stably balancing the influence of the high and low pressure difference on the spool.
- FIG. 2 is a schematic structural view of a specific embodiment of an expansion valve according to the present invention
- FIG. 3 is a cross-sectional view taken along line A-A of FIG.
- the expansion valve in this embodiment includes a valve body 13 having a chamber.
- the upper end of the valve body 13 is provided with a first opening 17 and a second opening 6.
- the first opening 17 and the second opening 6 further have a gas box head.
- the component and the transmission rod 5, the air box head part comprise a gas box cover 1, a diaphragm 2, a transmission piece 4 and a gas box seat 3.
- the first opening 17 is connected to the first nozzle, and the second opening 6 is connected to the second nozzle.
- the first opening 17 and the second opening 6 are both in communication with the chamber 19 of the valve body 13.
- the expansion valve further includes a valve body 15 and a valve seat 16 disposed in the chamber 19.
- the valve seat 16 may be formed by an inner step of the valve body 13.
- the valve seat 16 may also be independently disposed.
- the spool 15 is moved relative to the valve seat 16 to adjust the valve opening opening of the valve seat 16 to control the size of the flow passage between the first opening 17 and the second opening 6, the spool including the spool head facing the valve seat 151, further comprising a base portion 152 connected to the valve head portion 151, the side wall of the base portion 152 mating with the inner wall of the valve body 13, forming a guiding surface for the movement of the valve core 15, the valve core structure can be as shown in FIG.
- valve core 15 can move up and down relative to the valve seat 16 in the axial direction to adjust the valve opening opening size of the valve seat 16, thereby controlling the opening degree of the valve opening between the first opening 17 and the second opening 6; the lower end of the transmission rod 5 Acting on the upper surface of the spool base portion 152, the spool 15 is also supported by the reset structure.
- the adjusting spring 7 can be employed as the reset structure.
- a temperature sensing package (not shown) is arranged at the outlet of the evaporator, the temperature sensing package senses the evaporator outlet temperature, the temperature rises, and the working medium pressure in the temperature sensing package increases, and is transmitted to the diaphragm 2 through the capillary tube.
- FIG. 4 is an axial sectional view of the expansion valve spool shown in FIG. 3.
- FIG. 5 is a three-dimensional structural diagram of the valve core shown in FIG.
- the spool 15 has an axial through hole 1511 toward the head 151 of the valve seat 16, and the axial through hole 1511 may be an equal diameter hole connected to the end surface of the spool head 151 as shown in FIG. 4, and the axial through hole 1511
- the minimum cross-sectional area S2 is the cross-sectional area of the hole.
- the upper end surface of the spool head 151 facing the valve seat 16 is subjected to fluid pressure in the first opening 17, and when the spool head 151 is engaged with the valve seat 16, the spool face 1512 of the spool head 151 and the valve seat 16 With the sealing, the valve core surface 1512 may be a tapered side surface of the valve core head 151 shown in FIG. 4.
- the pressure of the valve core 15 in the first opening 17 is effective.
- the area is the cross-sectional area of the valve core surface 1512 toward the valve port side, that is, S1-S2; in the solution of the present invention, when the maximum flow area S1 at the valve port is constant, the spool axial through hole 1511
- the minimum cross-sectional area S2 is much larger than the cross-sectional area of the valve face 1512 toward the valve port side, that is, the cross-sectional area (S1-S2) of the valve face 1512 toward the valve port side is as small as possible.
- a piston 14 is disposed in the axial through hole 1511 of the spool head 151, and the piston 14 is connected to the valve body 13.
- the piston 14 is adapted to withstand the fluid pressure from the first opening 17, so that the piston 14 is preferably in sealing engagement with the bore wall of the spool head 151, and a sealing bore can be provided, while ensuring that the spool 15 can move up and down relative to the piston 14. .
- the force received by the piston 14 is proportional to the cross-sectional area S2 of the axial through hole 1511 of the spool 15.
- the high pressure fluid enters the inner cavity of the valve body 13 from the first nozzle, is throttled by the valve port of the valve seat 16, and then flows out from the second nozzle. Since the spool head 151 has an axial through hole 1511, and the minimum cross-sectional area S2 of the axial through hole 1511 is much larger than the cross-sectional area of the valve face 1512 toward the valve port side, the first opening 17 is obtained.
- the high pressure fluid pressure mainly acts on the upper surface of the piston 14 located in the axial through hole 1511 of the spool head 151. Since the piston 14 is connected to the valve body 13, the force received by the piston 14 is finally transmitted to the valve body 13 for balance. .
- the cross-sectional area of the spool face 1512 of the spool head 151 toward the valve port side is small, the high pressure fluid pressure from the first opening 17 produces only a small downward force to the spool 15. , the impact on the spool 15 is small.
- the chamber 19 and the second opening 6 corresponding to the lower end of the valve core base portion 152 are in communication with each other, and the low pressure from the second opening 6 can simultaneously act on the upper and lower end faces of the valve core base portion 152, and the spool
- the area of the upper and lower end faces of the base portion 152 is substantially equal, and therefore, the structure can also apply an additional force to the spool 15 on the side of the H-pressure.
- valve core 15 surface 1512 and the upper end surface of the piston 14 is the same as that of the refrigerant flowing from the first opening 17 to the second opening 6, and will not be described herein.
- FIG. 6 is a schematic structural view of another embodiment of the expansion valve according to the present invention
- FIG. 7 is an axial sectional view of the valve core shown in FIG.
- the axial through hole 1511 of the valve body 15 facing the valve seat 16 in this embodiment includes a small diameter hole connected to the end surface of the valve body head 151 and a large diameter hole which is connected with the small diameter hole to form a step, and the piston 14 is disposed on the large diameter In the hole. That is, the inner wall of the top end of the valve body 15 projects inwardly to form a downward annular step 1513, thereby forming a stepped hole-shaped axial through hole 1511.
- the minimum cross sectional area S2 of the axial through hole 1511 is It is the cross-sectional area of the small diameter hole.
- the cross-sectional area S2 of the small diameter hole of the spool axial through hole 1511 is much larger than the cross section of the valve face 1512 toward the valve port side.
- the area (i.e., S1-S2), the piston 14 still balances most of the pressure at the valve port of the valve seat 16 from the first opening 17. Therefore, this structure can balance the force exerted by the pressure of the first opening 17 on the spool 15.
- the minimum cross-sectional area S2 of the axial through hole 1511 is generally the maximum circulation at the valve port of the valve seat 16.
- the area S1 is 0.6 times or more (i.e., S2/S1 > 0.6)
- the effect of reducing the pressure of the spool 15 is preferably achieved.
- the minimum cross-sectional area S2 of the axial through hole 1511 is preferably a valve.
- the maximum flow area S1 at the valve port of the seat 16 is 0.9 times or more (i.e., S2/S1 > 0.9).
- the ratio of the minimum cross-sectional area S2 of the axial through hole 1511 to the maximum flow area S1 at the valve port is not limited to 0.6 or more, as long as the embodiment in which the force receiving area of the valve core surface 1512 is minimized can be achieved. It is within the scope of the invention.
- the spool base portion 152 may have an internal cavity on which the inner cavity and the second opening of the valve plug base portion 152 are disposed.
- Balance hole 1521 of 6 As shown in FIG. 4, the diameter of the valve core base portion 152 is larger than the diameter of the valve core head portion 151, and the joint portion forms a stepped surface, and the balance hole 1521 penetrating in the thickness direction thereof can be disposed on the step surface.
- the hole 1521 communicates with the second opening 6 and the inner cavity of the spool base portion 152.
- the high pressure or low pressure fluid from the second opening 6 can flow to the upper and lower end faces of the valve core base portion 152, and the areas of the upper and lower end faces of the valve core base portion 152 are substantially equal, so that the force balance of the valve body 15 can be achieved.
- the gap can communicate with the inner cavity of the second opening 6 and the valve core base portion 152, and the high pressure or low pressure fluid from the second opening 6 can also flow to the upper and lower end faces of the valve core base portion 152 to realize the receiving of the valve body 15. Balance of force.
- the piston 14 can be coupled to the support member 8 of the spool 15 via a piston connecting rod 18.
- the adjusting spring 74 connected to the spool 15 is connected to the support member 8
- the support member 8 is connected to the upper end of the adjusting rod 10
- the adjusting rod 10 is connected to the adjusting seat 9, the adjusting seat 9 and the valve
- the body 13 is fixed, so that the piston 14 is connected to the support member 8 via the piston connection 4, and the connection of the piston 14 to the valve body 13 is achieved.
- This type of connection of the piston 14 utilizes the support member 8 of the spool 15, and the process is tubular and the structure is more flexible.
- the piston 14 can also be connected to the valve body 13 by other means.
- a first external thread can be machined on the adjusting rod 10 of the expansion valve, and a first internal thread adapted to the first external thread is formed on the inner wall of the adjusting seat 9 of the expansion valve, and the position of the adjusting rod 10 can be fixed. It is also possible to adjust the axial position of the adjusting rod 10 by rotating the adjusting rod 10, thereby adjusting the position of the supporting member 8, finally adjusting the axial length of the adjusting spring 7, controlling the resetting ability of the spool 15, and the structure is more compact and flexible. Higher sex. It is also possible to further provide a ring groove on the peripheral wall of the adjusting rod 10, and a sealing seal 11 is built in the ring groove to achieve a seal between the adjusting rod 10 and the adjusting seat 9.
- the spiral groove can be machined at the bottom of the adjustment rod 10, and the rotation of the adjustment rod 10 can be realized by a simple tool such as a screwdriver, which facilitates the adjustment and adjustment of the rod 10.
- the adjusting seat 9 is usually inserted into the lower port of the valve body 13.
- a second external thread can be machined on the outer wall of the adjusting seat 9, on the inner wall of the valve body 13. Machining a second internal thread adapted to the second external thread, the adjustment seat 9 can It is conveniently fixed to the lower end of the valve body 13 by a threaded fit.
- FIG. 8 is an axial sectional view of the supporting member in the expansion valve shown in FIG. 2.
- FIG. 9 is a perspective structural view of the supporting member shown in FIG.
- the bottom of the support member 8 of the expansion valve is provided with a bottom groove 82.
- the bottom of the bottom groove 82 is recessed inwardly to form a tapered shape, which is adapted to the shape of the tip end of the adjustment rod 10, and the lower end surface of the bottom groove 82.
- the cross-sectional area of the portion other than the lower end surface of the bottom groove 82 is substantially equal to the cross-sectional area of the upper end of the adjusting rod 10, and the lower end of the adjusting rod 10 can be freely rotated in the bottom groove 82.
- the radial gap between the adjusting rod 10 and the inner wall of the bottom groove 82 should be as much as possible, preferably within 0.15 mm, and the adjusting rod 10 can be restrained while rotating or other adjusting action can be realized.
- the adjusting rod 10 is installed in the threaded hole of the adjusting seat 9 after the sealing jaw 11 is installed. Since the bottom groove 82 has an inner buckle structure, the upper end of the adjusting rod 10 can be pressed into the bottom groove of the supporting member 8. 82, thereby defining the adjustment rod 10 and the support member 8.
- the top recess 81 can be machined on the top of the support member 8, as shown in Fig. 8, the bottom of the top recess 81 is recessed inward, and the upper end of the top recess 81 Where the inner buckle is provided, the cross-sectional area of the portion other than the upper end surface of the top recess 81 is substantially equal to the cross-sectional area of the lower end of the piston connecting rod 18, and the lower end of the piston connecting rod 18 can be freely rotated in the top recess 81.
- the radial gap between the lower end of the piston connecting rod 18 and the inner wall of the top groove 81 should be as small as possible, and the radial gap can be controlled within 0.15 mm.
- the lower end of the piston connecting rod 18 can be press fitted into the top recess 81 of the support member 8.
- the axial clearance of the lower end of the support member 8 and the piston connection 4 and the axial clearance of the support member 8 and the adjustment rod 10 should be as small as possible, preferably within 0.5 mm.
- the support member 8 is press-fitted to the lower end of the piston connecting rod 18 or the support member 8 is press-fitted with the adjusting rod 10
- the axial tensile strength of the piston connecting rod 18, the supporting member 8 and the adjusting rod 10 should be able to withstand from The pressure at which the second opening 6 acts on the piston connecting rod 18.
- FIG. 10 is a schematic structural view of still another embodiment of the expansion valve according to the present invention.
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Description
一种膨胀阀 本申请要求于 2010 年 11 月 18 日提交中国专利局、 申请号为 201010551254.4、 发明名称为"一种膨胀阀"的中国专利申请的优先权, 其 全部内容通过引用结合在本申请中。 技术领域
本发明涉及制冷技术领域, 特别涉及一种膨胀阀。
背景技术
在制冷循环***回路中, 通常安装有膨胀阀, 膨胀阀通过感应制冷系 统中蒸发器出口或压缩机吸入段的过热度来控制阀的开度大小, 从而实现 ***制冷剂流量调节和节流降压的作用。
请参考图 1 , 图 1为一种典型的膨胀阀结构示意图。
膨胀阀通常具有入口管 900和出口管 400, 来自冷凝器的高压流体从 入口管 900进入, 节流降压后从出口管 400流向蒸发器。 膨胀阀的上端包 括气箱头 100以及传动杆 200, 传动杆 200连接阀芯 500, 阀座 1000位于 出口管 400与入口管 900的交接处, 阀芯 500与阀座 1000配合, 阀芯 500 通过弹簧 600与支撑部件 700抵接。
支撑部件 700的底部连接调节杆 800, 阀芯 500、支撑部件 700以及弹 簧 600位于阀壳内, 调节杆 800与调节座固定。
在蒸发器的出口处设有感温包, 感温包感应蒸发器出口温度, 温度过 高, 感温包内工质压力增大, 通过毛细管传递至气箱头内的膜片使其向下 运动, 带动传动杆 200推动阀芯 500离开阀座 1000, 则阀芯 500可以通过 感温包产生的压力控制入口管 900与出口管 400之间连接开口的大小。
此外, 高压冷凝压力通过入口管 900对阀芯 500产生使阀开启方向的 力, 来自出口管 400的蒸发压力对阀芯 500产生使其关闭方向的力, 因此, 阀芯 500除了要受到使阀芯 500开启的感温包压力以及使阀芯 500关闭的 蒸发压力和弹簧力之外, 还要额外承受由于高低压压差而对阀芯 500产生 的力。 对于小容量阀或低压制冷***来说, 高低压压差对阀芯 500的力对
***的影响较小, 但对于大容量阀或高压制冷***来说, 高低压压差对阀 芯 500的力对***的影响很大, 这样膨胀阀的过热度不能反映蒸发器真实 过热度, 会大大降低***的工作效率。 而且, 如果将该类结构膨胀阀用于 热泵等需要双向工作的***, 则制冷和制热时高低压压差对阀芯 500产生 的力是完全反向的, 这样不能使两个方向的静止过热度相同, 会使制冷或 制热的其中某一循环的工作效率降低的更加明显。
为解决以上问题, 现有技术中对阀芯 500结构作了一定的改进, 在阀 芯 500上加工出通孔, 对自入口管 900的压力可以由阀芯 500的内外端面 进行平衡。 然而,此种结构膨胀阀通过阀芯 500自身受力以实现受力平衡, 性能不够稳定, 且阀芯 500结构复杂, 重量大, 耗材多, 同时也会增加调 节弹簧 600的负载; 此外, 调节杆 800、 支撑部件 700连接复杂, 加工以 及装配较为麻烦。
因此, 如何提供一种更为稳定地平衡高低压差对阀芯影响的膨胀阀是 本领域技术人员目前需要解决的技术问题。 发明内容
本发明要解决的技术问题是提供一种膨胀阀, 该膨胀阀具备更为稳定 地平衡高低压差对阀芯影响的功能。
为解决上述技术问题,本发明提供一种膨胀阀, 包括具有腔室的阀体、 位于所述腔室内的阀座以及阀芯、与所述腔室连通的第一开口和第二开口, 所述阀芯相对于所述阀座移动以控制所述第一开口和所述第二开口之间的 流路通道的大小, 所述阀芯包括朝向所述阀座的阀芯头部, 所述阀芯头部 设有轴向通孔, 所述轴向通孔中设有活塞, 所述活塞与所述阀体连接。
优选地, 所述轴向通孔为与所述阀芯头部的端面连接的等径孔。
优选地, 所述轴向通孔包括与所述阀芯头部的端面连接的小径孔和与 所述小径孔连接构成台阶的大径孔, 所述活塞设置于所述大径孔中。
优选地, 所述轴向通孔的最小横截面积为所述阀座的阀口处的最大流 通面积的 0.6倍以上。
优选地, 所述轴向通孔的最小横截面积为所述阀座的阀口处的最大流
通面积的 0.9倍以上。
优选地, 所述阀芯头部连接有基座部, 所述基座部具有内腔, 且所述 基座部设有连通所述内腔与所述第二开口的平衡孔。
优选地, 所述轴向通孔的孔壁与所述活塞之间设置有密封部件。
优选地, 所述活塞通过活塞连接 4干连接在所述阀芯的支撑部件上。 优选地, 所述膨胀阀的调节杆上设有第一外螺纹, 所述膨胀阀的调节 座的内壁设有与所述第一外螺纹适配的第一内螺纹。
优选地, 所述支撑部件的底部具有供所述调节杆的上端压装入内的底 部 槽。
优选地, 所述支撑部件的底部具有与所述调节杆的顶端适配的凹孔。 优选地, 所述支撑部件顶部具有供所述活塞连接杆的下端压装入内的 顶部凹槽。
该发明所提供的膨胀阀的阀芯头部具有轴向通孔, 且轴向通孔中设有 活塞,活塞与所述阀体连接, 则作用于阀芯的流体压力主要由活塞来承受, 由于活塞与阀体连接, 则最终将压力传递至阀体, 由阀体来平衡。 因此, 流体的压力不影响阀芯的工作性能, 阀芯的开度都可以较为真实地反映蒸 发器出口过热度变化情况。 该膨胀阀运用了阀体自身来平衡受力, 可以更 为稳定地平衡高低压差对阀芯的影响。
附图说明
图 1为一种典型的膨胀阀结构示意图;
图 2为本发明所提供膨胀阀一种具体实施方式结构示意图;
图 3为图 2的 A-A向剖视图;
图 4为图 3所示膨胀阀阀芯的轴向剖面图;
图 5为图 4所示阀芯的立体结构示意图;
图 6为本发明所提供膨胀阀另一种具体实施方式的结构示意图; 图 7为图 6所示阀芯的轴向剖面图;
图 8为图 2所示膨胀阀中支撑部件的轴向剖视图;
图 9为图 8所示支撑部件的立体结构示意图;
图 10为本发明所提供膨胀阀又一种具体实施方式的结构示意图。
具体实施方式
本发明的核心是提供一种膨胀阀, 该膨胀阀具备更为稳定地平衡高低 压压差对阀芯影响的功能。
为了使本领域的技术人员更好地理解本发明的技术方案, 下面结合附 图和具体实施例对本发明作进一步的详细说明。
请参考图 2和图 3 , 图 2为本发明所提供膨胀阀一种具体实施方式的 结构示意图; 图 3为图 2的 A-A向剖视图。
该实施方式中的膨胀阀, 包括具有腔室的阀体 13 , 阀体 13的上端设 有第一开口 17以及第二开口 6, 第一开口 17与第二开口 6的上方还具有 气箱头部件以及传动杆 5 , 气箱头部件包括气箱盖 1、 膜片 2、 传动片 4和 气箱座 3。 第一开口 17连接第一接管, 第二开口 6连接第二接管, 第一开 口 17与第二开口 6均与阀体 13的腔室 19连通。
该膨胀阀还包括设于腔室 19中的阀芯 15和阀座 16, 如图 3所示, 上 述阀座 16可以由阀体 13的内台阶形成, 当然, 阀座 16也可以独立设置, 阀芯 15相对于阀座 16移动来调节阀座 16的阀口开启大小,以控制第一开 口 17和第二开口 6之间的流路通道大小, 阀芯包括朝向阀座的阀芯头部 151 , 还可以包括与阀芯头部 151连接的基座部 152, 基座部 152的侧壁与 阀体 13的内壁配合, 形成阀芯 15移动的导向面, 阀芯结构可以如图 4所 示,阀芯 15可以沿轴向相对于阀座 16上下运动来调节阀座 16的阀口开启 大小, 进而控制第一开口 17与第二开口 6之间阀口开度大小; 传动杆 5 下端作用于阀芯基座部 152上表面, 同时, 阀芯 15还由复位结构支撑, 如 图 3所示, 可以采用调节弹簧 7作为复位结构。 在蒸发器的出口设有感温 包(图中未示出), 感温包感应蒸发器出口温度, 温度升高, 感温包内工质 压力增大, 通过毛细管传递至膜片 2使其推动传动片 4向下运动, 进而带 动传动杆 5向下移动,传动杆 5再推动阀芯 15克服调节弹簧 7的弹力以及 蒸发压力对膜片产生的使阀芯 15朝关闭方向移动的力而离开阀座 16, 从 而增大阀座 16的阀口开度,增加通过的制冷剂流量;蒸发器出口温度降低,
感温包内工质压力下降, 则与上述过程相反, 在蒸发压力和调节弹簧 7的 复位弹力作用下, 阀芯 15往阀座 16方向移动,从而减小第一开口 17与第 二开口 6之间的阀口开度, 减少通过的制冷剂流量。
请参考图 4和图 5, 图 4为图 3所示膨胀阀阀芯的轴向剖面图; 图 5 为图 4所示阀芯的立体结构示意图。
阀芯 15朝向阀座 16的头部 151具有轴向通孔 1511 , 轴向通孔 1511 可以是如图 4所示的与阀芯头部 151端面连接的等径孔, 其轴向通孔 1511 的最小横截面积 S2即为该孔的横截面积。 阀芯头部 151朝向阀座 16的上 端面需承受第一开口 17内的流体压力,当阀芯头部 151与阀座 16配合时, 阀芯头部 151的阀芯面 1512与阀座 16配合密封,上述阀芯面 1512可以是 图 4所示的阀芯头部 151的锥形侧面, 如设阀口处的最大流通面积为 S1 , 则阀芯 15 受第一开口 17内压力的有效面积为阀芯面 1512朝向阀口一侧 的横截面积, 即 S1-S2; 在本发明的方案中, 当阀口处的最大流通面积 S1 为一定的条件下, 阀芯轴向通孔 1511 的最小横截面积 S2远大于阀芯面 1512朝向阀口一侧的横截面积, 即阀芯面 1512朝向阀口一侧的横截面积 ( S1-S2 )尽量小。 阀芯头部 151的轴向通孔 1511内设有活塞 14, 活塞 14 与阀体 13连接。 活塞 14用于承受来自第一开口 17的流体压力, 因此, 活 塞 14最好与阀芯头部 151的孔壁密封配合,可以设置密封圏, 同时需保证 阀芯 15可相对于活塞 14上下运动。 活塞 14所^受的力与阀芯 15的轴向 通孔 1511的横截面积 S2成正比。
当制冷剂从第一开口 17流向第二开口 6时,高压流体从第一接管进入 阀体 13的内腔, 通过阀座 16的阀口节流降压后, 从第二接管流出。 由于 阀芯头部 151具有轴向通孔 1511 , 且上述轴向通孔 1511的最小横截面积 S2远大于阀芯面 1512朝向阀口一侧的横截面积, 因此, 来自第一开口 17 的高压流体压力主要作用在位于阀芯头部 151轴向通孔 1511 内的活塞 14 的上表面, 由于活塞 14与阀体 13连接, 则活塞 14所受的力最终传递至阀 体 13上进行平衡。 同时, 由于阀芯头部 151的阀芯面 1512朝向阀口一侧 的横截面积很小, 因此, 来自第一开口 17的高压流体压力仅对阀芯 15产 生较小的方向向下的力, 对阀芯 15的影响较小。
此外,阀芯基座部 152下端对应的腔室 19与第二开口 6是相互连通的, 则来自第二开口 6的低压压力可以同时作用在阀芯基座部 152的上下端面, 而阀芯基座部 152上下端面的面积基本相等, 因此, 该结构也可以平 H氐 压侧对阀芯 15产生的附加力。
当制冷剂从第二开口 6流向第一开口 17时,高压流体从第二接管进入 阀体 13内, 高压流体压力分别作用于阀芯基座部 152上下端面,可以自动 平衡;低压侧流体压力作用在阀芯 15阀芯面 1512和活塞 14上端面, 与上 述制冷剂从第一开口 17流向第二开口 6时的原理相同, 在此不再赘述。
请参考图 6和图 7, 图 6为本发明所提供膨胀阀另一种具体实施方式 的结构示意图; 图 7为图 6所示阀芯的轴向剖面图。
该具体实施方式中的阀芯 15朝向阀座 16的轴向通孔 1511包括与阀芯 头部 151的端面连接的小径孔和与小径孔连接构成台阶的大径孔, 活塞 14 设置于大径孔中。 即阀芯 15 的顶端内壁向内凸出形成向下的环形台阶 1513 ,既而形成阶梯孔状的轴向通孔 1511 ,在该实施例中,其轴向通孔 1511 的最小横截面积 S2即为小径孔的横截面积。与上述实施方式相同, 当阀口 处的最大流通面积 S1为一定的条件下, 阀芯轴向通孔 1511的小径孔的横 截面积 S2远大于阀芯面 1512朝向阀口一侧的横截面积(即 S1-S2 ) , 活塞 14依然平衡了大部分来自第一开口 17的阀座 16的阀口处的压力。 因此, 此结构可以平衡第一开口 17的压力对阀芯 15产生的作用力。
对于以上实施方式, 为了尽量减小第一开口 17处流体对阀芯 15的作 用力,一般情况下, 当轴向通孔 1511的最小横截面积 S2为阀座 16的阀口 处的最大流通面积 S1的 0.6倍以上(即 S2/S1 > 0.6 )时, 即可以起到较好 的减小阀芯 15压力的效果, 优选地, 轴向通孔 1511 的最小横截面积 S2 最好为阀座 16的阀口处的最大流通面积 S1的 0.9倍以上(即 S2/S1 > 0.9 )。 当然, 这里并不是将轴向通孔 1511的最小横截面积 S2与阀口处的最大流 通面积 S1的比例限定为 0.6以上, 只要能实现尽量减小阀芯面 1512受力 面积的实施例均在本发明的保护范围之内。
为了更好地平衡来自第二开口 6内流体的压力, 阀芯基座部 152可以 具有内腔, 在阀芯基座部 152上设置连通阀芯基座部 152内腔和第二开口
6的平衡孔 1521。 如图 4所示, 阀芯基座部 152的直径大于阀芯头部 151 的直径, 二者连接处形成台阶面, 可以在台阶面上设置沿其厚度方向贯穿 的平衡孔 1521 , 则该平衡孔 1521连通第二开口 6以及阀芯基座部 152的 内腔。因此,来自第二开口 6的高压或低压流体均可以流至阀芯基座部 152 的上下端面, 阀芯基座部 152上下端面的面积基本相等, 从而可以实现阀 芯 15的受力平衡。
还可以使阀芯基座部 152的外侧壁与阀体 13的内壁之间存在间隙。则 此间隙可以连通第二开口 6与阀芯基座部 152的内腔, 同样可以使来自第 二开口 6的高压或低压流体流至阀芯基座部 152上下端面, 实现阀芯 15 的受力平衡。
活塞 14可以通过活塞连接杆 18连接在阀芯 15的支撑部件 8上。如图 2所示, 与阀芯 15连接的调节弹簧 7 4氏接在支撑部件 8上, 支撑部件 8与 调节杆 10的上端连接, 而调节杆 10与调节座 9连接, 调节座 9与阀体 13 固定, 因此, 将活塞 14通过活塞连接 4干 18连接于支撑部件 8, 实现了活 塞 14与阀体 13的连接。 活塞 14的此种连接方式, 运用了阀芯 15的支撑 部件 8, 工艺得以筒化, 结构更为灵活。 当然, 活塞 14也可以通过其他方 式与阀体 13连接。
可以在膨胀阀的调节杆 10上加工出第一外螺纹, 在膨胀阀的调节座 9 的内壁上加工出与第一外螺纹适配的第一内螺纹, 不但可以固定调节杆 10 的位置, 还可以通过旋转调节杆 10调整调节杆 10的轴向位置, 进而调整 支撑部件 8的位置,最终调整调节弹簧 7的轴向长度,控制阀芯 15的复位 能力, 结构更为筒单, 且灵活性较高。 还可以进一步地在调节杆 10的周壁 上设置环槽, 内置密封圏 11于环槽内, 实现调节杆 10与调节座 9之间的 密封。
可以在调节杆 10的底部加工出螺旋槽,则通过螺丝刀等筒易工具即可 实现调节杆 10的旋转, 方便调节杆 10的安装以及调整。
调节座 9通常插接在阀体 13 的下部端口, 为了进一步加强调节座 9 与阀体 13的固定以及便于安装,可以在调节座 9的外壁加工出第二外螺纹, 在阀体 13的内壁加工出与第二外螺纹适配的第二内螺纹,则调节座 9可以
方便地通过螺纹配合与阀体 13的下端连接固定。
请参考图 8和图 9, 图 8为图 2所示膨胀阀中支撑部件的轴向剖视图; 图 9为图 8所示支撑部件的立体结构示意图。
膨胀阀的支撑部件 8的底部设有底部 槽 82, 如图 8所示, 底部 槽 82的底部向内凹进, 形成锥状, 与调节杆 10的顶端形状相适应, 底部凹 槽 82下端面处具有内扣的结构, 底部凹槽 82下端面以外部分的横截面积 与调节杆 10上端的横截面积基本相当, 在保证调节杆 10的下端可以在底 部凹槽 82内自由转动的情况下,调节杆 10与底部凹槽 82内壁之间的径向 间隙应该尽量 d、, 最好在 0.15mm以内, 则调节杆 10得以限位的同时, 还 可以实现旋转或是其他调整动作。 安装时, 调节杆 10安装密封圏 11后先 安装在调节座 9的螺纹孔中, 由于底部凹槽 82存在内扣结构, 则可以将调 节杆 10的上端压装入支撑部件 8的底部凹槽 82,从而限定调节杆 10与支 撑部件 8。
与上述调节杆 10与支撑部件 8的固定方式类似, 可以在支撑部件 8 的顶部加工顶部凹槽 81 , 如图 8所示, 顶部凹槽 81的底部向内凹进, 顶 部凹槽 81上端面处具有内扣的结构, 顶部凹槽 81上端面以外部分的横截 面积与活塞连接杆 18下端的横截面积基本相当, 在保证活塞连接杆 18下 端可以在顶部凹槽 81内自由转动的情况下, 活塞连接杆 18下端与顶部凹 槽 81内壁之间的径向间隙应该尽量小, 可以将径向间隙控制在 0.15mm以 内, 安装时, 由于顶部凹槽 8上端面处存在内扣结构, 可以将活塞连接杆 18的下端压装入支撑部件 8的顶部凹槽 81内。
此外, 支撑部件 8与活塞连接 4干 18下端的轴向间隙加上支撑部件 8 与调节杆 10的轴向间隙应尽量小,最好控制在 0.5mm以内。 当支撑部件 8 与活塞连接杆 18下端进行压装连接或者支撑部件 8与调节杆 10进行压装 连接时, 活塞连接杆 18、 支撑部件 8以及调节杆 10的轴向拉伸强度应能 承受来自第二开口 6作用在活塞连接杆 18上的压力。
请参考图 10, 图 10为本发明所提供膨胀阀又一种具体实施方式的结 构示意图。
还可以在支撑部件 8的底部加工出具有与调节杆 10顶端相适配凹孔
83 , 则安装时, 可以直接将调节杆 10顶端装入凹孔 83 , 则调节杆 10可以 与支撑部件 8底部 4氏接在一起。此种结构适用于第一开口 17流向第二开口 6的单向流动情形, 支撑部件 8受到向下的压力, 因此, 调节杆 10的顶端 与支撑部件 8底部的 孔 83不会脱离,此种结构筒化了支撑部件 8底部的 结构, 也筒化了安装工序。
以上对本发明所提供的一种膨胀阀进行了详细介绍。 本文中应用了具 体实施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
1、一种膨胀阀, 包括具有腔室(19)的阀体(13)、位于所述腔室(19) 内的阀座(16) 以及阀芯 (15)、 与所述腔室 (19)连通的第一开口 (17) 和第二开口 (6), 所述阀芯 (15)相对于所述阀座(16)移动以控制所述 第一开口(17)和所述第二开口(6)之间的流路通道的大小, 其特征在于, 所述阀芯( 15 )包括朝向所述阀座的阀芯头部( 151 ), 所述阀芯头部( 151 ) 设有轴向通孔(1511), 所述轴向通孔(1511) 中设有活塞(14), 所述活 塞(14)与所述阀体(13)连接。
2、根据权利要求 1所述的膨胀阀,其特征在于,所述轴向通孔( 1511 ) 为与所述阀芯头部 (151) 的端面连接的等径孔。
3、根据权利要求 1所述的膨胀阀,其特征在于,所述轴向通孔( 1511 ) 包括与所述阀芯头部( 151 )的端面连接的小径孔和与所述小径孔连接构成 台阶的大径孔, 所述活塞( 14)设置于所述大径孔中。
4、根据权利要求 1至 3任一项所述的膨胀阀, 其特征在于, 所述轴向 通孔(1511) 的最小横截面积(S2) 为所述阀座(16) 的阀口处的最大流 通面积(S1 ) 的 0.6倍以上。
5、根据权利要求 4所述的膨胀阀,其特征在于,所述轴向通孔( 1511 ) 的最小横截面积(S2) 为所述阀座(16) 的阀口处的最大流通面积(S1) 的 0.9倍以上。
6、 根据权利要求 4所述的膨胀阀, 其特征在于, 所述阀芯头部(151) 连接有基座部(152), 所述基座部(152)具有内腔, 且所述基座部(152) 设有连通所述内腔与所述第二开口 (6) 的平衡孔(1521)。
7、根据权利要求 4所述的膨胀阀,其特征在于,所述轴向通孔( 1511 ) 的孔壁与所述活塞(14)之间设置有密封部件。
8、 根据权利要求 4所述的膨胀阀, 其特征在于, 所述活塞( 14 )通过 活塞连接杆 (18)连接在所述阀芯 (15) 的支撑部件(8)上。
9、根据权利要求 8所述的膨胀阀, 其特征在于, 所述膨胀阀的调节杆 ( 10)上设有第一外螺纹, 所述膨胀阀的调节座(9)的内壁设有与所述第 一外螺纹适配的第一内螺纹。
10、 根据权利要求 8所述的膨胀阀, 其特征在于, 所述支撑部件 (8) 的底部具有供所述调节杆(10) 的上端压装入内的底部凹槽(82)。
11、 根据权利要求 8所述的膨胀阀, 其特征在于, 所述支撑部件 (8) 的底部具有与所述调节杆(10) 的顶端适配的凹孔(83)。
12、 根据权利要求 8所述的膨胀阀, 其特征在于, 所述支撑部件 (8) 顶部具有供所述活塞连接杆 (18) 的下端压装入内的顶部凹槽(81)。
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EP20110824294 EP2482009B1 (en) | 2010-11-18 | 2011-06-20 | Expansion valve |
US13/509,771 US9109822B2 (en) | 2010-11-18 | 2011-06-20 | Expansion valve |
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CN114754157A (zh) * | 2022-04-29 | 2022-07-15 | 中国电子科技集团公司第十四研究所 | 一种应用于两相流***的防过热动态流量调节装置 |
CN114763843A (zh) * | 2021-01-13 | 2022-07-19 | 浙江盾安人工环境股份有限公司 | 电子膨胀阀 |
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US9109822B2 (en) | 2015-08-18 |
CN102466377B (zh) | 2014-10-29 |
US20130227980A1 (en) | 2013-09-05 |
CN102466377A (zh) | 2012-05-23 |
EP2482009B1 (en) | 2014-10-22 |
EP2482009A1 (en) | 2012-08-01 |
EP2482009A4 (en) | 2013-04-17 |
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