WO2017193855A1 - 膨胀开关阀 - Google Patents

膨胀开关阀 Download PDF

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Publication number
WO2017193855A1
WO2017193855A1 PCT/CN2017/082946 CN2017082946W WO2017193855A1 WO 2017193855 A1 WO2017193855 A1 WO 2017193855A1 CN 2017082946 W CN2017082946 W CN 2017082946W WO 2017193855 A1 WO2017193855 A1 WO 2017193855A1
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WO
WIPO (PCT)
Prior art keywords
valve
inlet
outlet
port
expansion switch
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/CN2017/082946
Other languages
English (en)
French (fr)
Inventor
黄健
陈雪峰
叶梅娇
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.)
BYD Co Ltd
Original Assignee
BYD 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 CN201620419014.1U external-priority patent/CN205978641U/zh
Priority claimed from CN201610305624.3A external-priority patent/CN107355570A/zh
Application filed by BYD Co Ltd filed Critical BYD Co Ltd
Priority to EP17795473.2A priority Critical patent/EP3453929A4/en
Priority to US16/300,431 priority patent/US20190257560A1/en
Publication of WO2017193855A1 publication Critical patent/WO2017193855A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/325—Expansion valves having two or more valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2600/2515—Flow valves
    • 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 present disclosure relates to the field of control valves and, in particular, to an expansion switch valve.
  • the prior art uses a structure in which an electronic expansion valve and an electromagnetic switching valve are connected in parallel. This structure requires two three-way joints and six pipelines, which are complicated in structure and inconvenient to install.
  • the solenoid valve is closed and the electronic expansion valve is used, the electronic expansion valve inlet is a medium-temperature high-pressure liquid refrigerant, and the electronic expansion valve outlet is a low-temperature low-pressure liquid refrigerant.
  • the inlet and outlet of the solenoid valve are also respectively The state of the refrigerant in the inlet and outlet of the electronic expansion valve is the same, and the refrigerant pressure at the inlet and outlet of the solenoid valve is different, which easily causes damage to the internal structure of the solenoid valve.
  • the refrigerant charge of the entire heat pump system is increased and the cost is increased.
  • the heat pump system is operated at low temperatures, it is difficult to return the oil to the compressor. This complicated structure is also detrimental to the oil return of the heat pump system.
  • an expansion switch valve including a valve body, wherein the valve body is formed with an inlet, an outlet, and an internal flow passage communicating between the inlet and the outlet, the internal flow a first spool in which the inlet and the outlet are in direct communication or disconnected communication, and a second spool in which the inlet and the outlet pass through a section The flow port is connected or disconnected.
  • the internal flow passage includes a first flow passage and a second flow passage respectively communicating with the inlet, and the first flow passage is formed with a first valve port that cooperates with the first valve core
  • the throttle port is formed on the second flow path to form a second valve port that cooperates with the second valve body, and the first flow path and the second flow path meet at the second valve Downstream of the mouth and in communication with the outlet.
  • the second flow path is opened in the same direction as the outlet, and the first flow path is formed as a first through hole perpendicular to the second flow path, and the inlet is opened in a second through hole on the sidewall of the second flow channel is in communication with the second flow channel, and the first through hole and the second through hole are respectively communicated with the inlet.
  • the inlet and the outlet are opened perpendicular to each other on the valve body.
  • the first spool is coaxially disposed with the first valve port in a moving direction to selectively block or disengage the first valve port.
  • the second spool is coaxially disposed with the second valve port in a moving direction to selectively block or disengage the second valve port.
  • the first valve body includes a first valve stem and a first plug connected to an end of the first valve stem, the first plug for sealing against the first The end surface of the valve port blocks the first flow path.
  • the second valve body includes a second valve stem, the end of the second valve stem is formed as a conical head structure, and the second valve port is formed to be in phase with the conical head structure Fitted tapered hole structure.
  • the valve body includes a valve seat forming the internal flow passage and a first valve housing and a second valve housing mounted on the valve seat, and the first valve housing is mounted therein for Driving a first electromagnetic driving portion of the first valve body, a second electromagnetic driving portion for driving the second valve core is mounted in the second valve housing, the first valve core is from the first valve A shell extends to the inner flow passage within the valve seat, the second spool extending from the second valve housing to the inner flow passage within the valve seat.
  • the valve seat is formed in a polyhedral structure, and the first valve housing, the second valve housing, the inlet, and the outlet are respectively disposed on different surfaces of the polyhedral structure, wherein The mounting directions of the first valve housing and the second valve housing are perpendicular to each other, and the opening directions of the inlet and the outlet are perpendicular to each other.
  • the on-off control and/or the throttle expansion control function of the refrigerant can be realized, and the structure is simple, and the production and installation are easy.
  • the pipe connection can be simplified to reduce the cost, and the refrigerant charge amount of the entire heat pump system can be reduced, and the compressor can be returned to the oil.
  • FIG. 1 is a schematic top plan view of an expansion switch valve according to a preferred embodiment of the present disclosure
  • Figure 2 is a cross-sectional structural view taken along line AB-AB of Figure 1, wherein the first valve port and the second valve port are both in an open state;
  • FIG. 3 is a schematic front elevational view of the expansion switch valve according to a preferred embodiment of the present disclosure along a viewing angle;
  • Figure 4 is a cross-sectional structural view taken along line AB-AB of Figure 1, wherein the first valve port is in an open state and the second valve port is in a closed state;
  • Figure 5 is a cross-sectional structural view taken along line AB-AB of Figure 1, wherein the first valve port is in a closed state, and the second valve port is in an open state;
  • FIG. 6 is a front elevational view of the expansion switch valve according to a preferred embodiment of the present disclosure along another perspective;
  • Figure 7 is a cross-sectional structural view taken along line AC-AC of Figure 6, wherein the first valve port is in an open state and the second valve port is in a closed state;
  • FIG. 8 is a first internal structural diagram of an expansion switch valve according to a preferred embodiment of the present disclosure, wherein the first valve port and the second valve port are both in an open state;
  • Figure 9 is a partial enlarged view of a portion A of Figure 8.
  • FIG. 10 is a second internal structural diagram of an expansion switch valve according to a preferred embodiment of the present disclosure, wherein the first valve port is in an open state and the second valve port is in a closed state;
  • FIG. 11 is a schematic diagram of a third internal structure of an expansion switch valve according to a preferred embodiment of the present disclosure, wherein the first valve port is in a closed state and the second valve port is in an open state.
  • orientation words used such as “up, down, left, and right" are generally relative to the drawing direction of the drawing, and the "upstream, downstream” is relative to The medium, for example, in the flow direction of the refrigerant, specifically, the flow direction toward the refrigerant is downstream, and the flow direction away from the refrigerant is upstream, and "inside and outside” means the inside and outside of the contour of the corresponding member.
  • the present disclosure provides an expansion switch valve including a valve body 500, wherein the valve body 500 is formed with an inlet 501, an outlet 502, and an internal flow passage communicating between the inlet 501 and the outlet 502, the interior
  • a first spool 503 and a second spool 504 are mounted on the flow passage.
  • the first spool 503 directly connects or disconnects the inlet 501 and the outlet 502, and the second spool 504 allows the inlet 501 and the outlet 502 to pass through the orifice 505. Connect or disconnect.
  • the "direct communication" achieved by the first spool means that the refrigerant entering from the inlet 501 of the valve body 500 can flow directly to the outlet 502 of the valve body 500 through the internal flow passage without passing through the first spool.
  • the "disconnected communication” achieved by the first spool means that the refrigerant entering from the inlet 501 of the valve body 500 cannot pass over the first spool and cannot flow through the internal passage to the outlet 502 of the valve body 500.
  • the “connected through the orifice” achieved by the second spool means that the refrigerant entering from the inlet 501 of the valve body 500 can flow over the second spool and flow through the orifice to the outlet 502 of the valve body 500.
  • the “disconnected communication” achieved by the second spool means that the refrigerant entering from the inlet 501 of the valve body 500 cannot pass over the second spool and cannot flow through the orifice 505 to the outlet 502 of the valve body 500.
  • the expansion switch valve of the present disclosure can cause the refrigerant entering from the inlet 501 to achieve at least three states. That is, 1) an off state; 2) a direct communication state over the first valve body 503; and 3) a throttle communication mode over the second valve body 504.
  • the high-temperature high-pressure liquid refrigerant can be a low-temperature low-pressure mist-like liquid refrigerant after being throttled through the orifice 505, which can create conditions for the evaporation of the refrigerant, that is, the cross-sectional area of the orifice 505 is smaller than the outlet.
  • the cross-sectional area of 502, and by controlling the second spool, the opening degree of the orifice 505 can be adjusted to control the flow rate through the orifice 505, to prevent insufficient refrigeration due to too little refrigerant, and to prevent Excessive refrigerant causes the compressor to produce a liquid hammer phenomenon. That is, the cooperation of the second spool 504 and the valve body 500 can cause the expansion switch valve to function as an expansion valve.
  • the expansion switch valve provided by the present disclosure can reduce the refrigerant charge of the entire heat pump system, reduce the cost, simplify the pipeline connection, and facilitate the oil return of the heat pump system.
  • the valve body 500 includes a valve seat 510 forming an internal flow passage, and a first valve housing 511 mounted on the valve seat 510 and a second valve housing 512, a first electromagnetic driving portion 521 for driving the first valve body 503 is mounted in the first valve housing 511, and a second electromagnetic driving portion for driving the second valve core 504 is mounted in the second valve housing 512.
  • the first spool 503 extends from the first valve housing 511 to the internal flow passage in the valve seat 510
  • the second spool 504 extends from one end adjacent to the second valve housing 512 to the internal flow passage in the valve seat 510.
  • the position of the first valve core 503 can be conveniently controlled by controlling the on/off power of the first electromagnetic driving portion 521 (eg, the electromagnetic coil), thereby controlling the direct connection or disconnection of the inlet 501 and the outlet 502;
  • the control of the on/off of the second electromagnetic driving portion 522 e.g., the electromagnetic coil
  • the electronic expansion valve and the solenoid valve sharing the inlet 501 and the outlet 502 are installed in parallel in the valve body 500, thereby enabling automatic control of the on/off and/or throttling of the expansion switch valve, and simplifying the course of the pipe.
  • the valve seat 510 is formed into a polyhedral structure, the first valve housing 511, the second valve housing 512, the inlet 501 and the outlet 502 Minute They are not disposed on different surfaces of the polyhedral structure, wherein the mounting directions of the first valve housing 511 and the second valve housing 512 are perpendicular to each other, and the opening directions of the inlet 501 and the outlet 502 are perpendicular to each other.
  • the inlet and outlet pipes can be connected to different surfaces of the polyhedral structure, which can avoid the problem of messy and entangled pipe arrangement.
  • the internal flow path includes a first flow path 506 and a second flow path 507 respectively communicating with the inlet 501, and the first flow path 506 is formed with
  • the first valve port 503 is engaged with the first valve port 516, and the throttle port 505 is formed on the second flow path 507 to form a second valve port 517 that cooperates with the second valve body 504, the first flow path 506 and the second flow Lane 507 meets downstream of second valve port 517 and is in communication with outlet 502.
  • the closing or opening of the first valve port 516 is achieved by changing the position of the first valve body 503, thereby controlling the cutting or conduction of the first flow path 506 connecting the inlet 501 and the outlet 502, so that the above described The function of connecting or disconnecting the solenoid valve.
  • the cutting or conduction of the second valve port 517 is realized by changing the position of the second valve body 504, so that the throttle function of the electronic expansion valve can be realized.
  • the first flow path 506 and the second flow path 507 can communicate with the inlet 501 and the outlet 502 respectively in any suitable arrangement.
  • the second flow path 507 is the same as the outlet 502.
  • the first flow path 506 is formed as a first through hole 526 perpendicular to the second flow path 507, and the inlet 501 is connected to the second flow path 507 through the second through hole 527 opened in the sidewall of the second flow path 507.
  • the first through hole 526 and the second through hole 527 are respectively in communication with the inlet 501.
  • the first through hole 526 can be disposed in a vertical direction or in parallel with the second through hole 527, which is not limited by the disclosure, and is all within the protection scope of the present disclosure.
  • the inlet 501 and the outlet 502 are perpendicular to each other on the valve body 500.
  • the axis of the inlet 501, the axis of the outlet 502 (i.e., the axis of the second flow path 507), and the axis of the first flow path 506 are vertically arranged in space, thereby preventing the first
  • the movement of the spool 503 and the second spool 504 causes interference and the internal space of the valve body 500 can be utilized to the maximum.
  • the first valve core 503 is coaxially disposed with the first valve port 516 in the moving direction to selectively block or disengage the first valve. Port 516.
  • the second spool 504 is disposed coaxially with the second valve port 517 in the direction of movement to selectively block or disengage the second valve port 517.
  • the first valve core 503 may include a first valve stem 513 and a first end connected to the first valve stem 513 .
  • the second spool 504 includes a second valve stem 514, the end of which is tapered.
  • the head structure, the second valve port 517 is formed as a tapered hole structure that cooperates with the tapered head structure.
  • the opening degree of the expansion port 505 of the expansion switch valve can be adjusted by the up and down movement of the second valve core 504, and the The up and down movement of the two spools 504 can be adjusted by the second electromagnetic driving portion 522. If the opening of the orifice 505 of the expansion switch valve is zero, as shown in FIG. 4, the second spool 504 is at the lowest position, and the second spool 504 blocks the second valve port 517, and the refrigerant is completely unable to pass the throttle. Port 505, that is, the second valve port 517; if the expansion switch valve throttle port 505 has an opening degree, as shown in FIG.
  • the second solenoid 504 can be moved upward by controlling the second electromagnetic driving portion 522 to make the tapered head structure away from the throttle opening 505, thereby realizing the throttle opening 505.
  • the opening degree becomes larger; on the contrary, when it is required to reduce the opening degree of the orifice 505 of the expansion switching valve, the second valve body 504 can be driven to move downward.
  • the first valve core 503 is separated from the first valve port 516, and the first valve port 516 is in an open state,
  • the second valve core 504 is at the lowest position, the second valve core 504 blocks the throttle port 505, and the refrigerant flowing from the inlet 501 to the internal flow passage cannot pass through the throttle port 505 at all, and can only pass through the first valve port 516 in sequence.
  • the first through hole 526 flows into the outlet 502.
  • the first spool 503 moves to the left, the first plug 523 and the first valve port 516 are separated, the refrigerant can pass through the first through hole 526; when the solenoid valve is energized, the first spool 503 Moving to the right, the first plug 523 and the first valve port 516 are fitted together, and the refrigerant cannot pass through the first through hole 526.
  • dashed arrows with arrows in FIGS. 4 and 10 represent the flow path and the direction of the refrigerant when the solenoid valve function is used.
  • the second valve port 517 that is, the throttle port 505 is in an open state
  • the first valve body 503 blocks the first valve port 516.
  • the refrigerant flowing from the inlet 501 to the internal flow passage cannot pass through the first through hole 526, and can only flow into the outlet 502 through the second through hole 527 and the throttle port 505 in sequence, and can move the second valve core 504 up and down.
  • the size of the opening of the orifice 505 is adjusted.
  • dashed arrows with arrows in FIGS. 5 and 11 represent the flow path and the tendency of the refrigerant when the electronic expansion valve function is used.
  • the first spool 503 Deviating from the first valve port 516, the first valve port 516 is in an open state, the throttle port 505 is in an open state, and the refrigerant flowing into the inner flow channel can flow along the first flow channel 506 and the second flow channel 507 to the outlet 502, respectively, thereby It also has a solenoid valve function and an electronic expansion valve function.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Multiple-Way Valves (AREA)

Abstract

一种膨胀开关阀，包括阀体（500），该阀体上形成有进口（501）、出口（502）以及连通在该进口（501）和出口（502）之间的内部流道，该内部流道上安装有第一阀芯（503）和第二阀芯（504），该第一阀芯（503）使得该进口（501）和出口（502）直接连通或断开连通，该第二阀芯（504）使得该进口（501）和出口（502）通过节流口（505）连通或断开连通。这样通过在同一阀体的内部流道上集成安装第一阀芯（503）和第二阀芯（504），能够实现制冷剂的通断控制和/或节流膨胀控制功能，结构简单，易于生产和安装，且当该膨胀开关阀应用于热泵系统时，可以简化管路连接，降低成本，并且减少整个热泵系统的制冷剂充注量，便于压缩机回油。

Description

膨胀开关阀 技术领域
本公开涉及控制阀领域，具体地，涉及一种膨胀开关阀。
背景技术
热泵系统中有时需要控制制冷剂节流降压或者只通过不节流，而现有的电子膨胀阀只能控制制冷剂节流或者不通过。为满足热泵系统的这种需求，现有技术要用到电子膨胀阀和电磁开关阀并联的结构。这种结构需要用到两个三通接头、六根管路，结构比较复杂，不便于安装。当电磁阀关闭，使用电子膨胀阀时，电子膨胀阀进口为中温高压的液态制冷剂，电子膨胀阀出口为低温低压的液态制冷剂，由于管路是连通的，所以电磁阀的进出口也分别跟电子膨胀阀进出口的制冷剂状态一致，电磁阀进出口的制冷剂压力温度不一样，容易对电磁阀的内部结构造成损坏。另外，由于管路比较多，会提高整个热泵系统的制冷剂充注量，提高成本。热泵系统在低温下工作时，压缩机回油会比较困难，这种复杂的结构还会不利于热泵系统的回油。
发明内容
本公开的目的是提供一种膨胀开关阀，该膨胀开关阀能够实现对流经媒介的通断控制和节流控制两种功能，且结构简单。
为了实现上述目的，本公开提供一种膨胀开关阀，包括阀体，其中，该阀体上形成有进口、出口以及连通在所述进口和所述出口之间的内部流道，所述内部流道上安装有第一阀芯和第二阀芯，所述第一阀芯使得所述进口和所述出口直接连通或断开连通，所述第二阀芯使得所述进口和所述出口通过节流口连通或断开连通。
根据本公开的一个实施例，所述内部流道包括分别与所述进口连通的第一流道和第二流道，所述第一流道上形成有与所述第一阀芯配合的第一阀口，所述节流口形成在所述第二流道上以形成为与所述第二阀芯配合的第二阀口，所述第一流道和所述第二流道交汇于所述第二阀口的下游并与所述出口连通。
根据本公开的一个实施例，所述第二流道与所述出口同向开设，所述第一流道形成为与所述第二流道相互垂直的第一通孔，所述进口通过开设在所述第二流道侧壁上的第二通孔与所述第二流道连通，所述第一通孔和所述第二通孔与所述进口分别连通。
根据本公开的一个实施例，所述进口与所述出口相互垂直地开设在所述阀体上。
根据本公开的一个实施例，所述第一阀芯沿移动方向与所述第一阀口同轴布设以可选择地封堵或脱离所述第一阀口。
根据本公开的一个实施例，所述第二阀芯沿移动方向与所述第二阀口同轴布设以可选择地封堵或脱离所述第二阀口。
根据本公开的一个实施例，所述第一阀芯包括第一阀杆和连接在该第一阀杆端部的第一堵头，该第一堵头用于密封压靠在所述第一阀口的端面上以封堵所述第一流道。
根据本公开的一个实施例，所述第二阀芯包括第二阀杆，该第二阀杆的端部形成为锥形头结构，所述第二阀口形成为与该锥形头结构相配合的锥形孔结构。
根据本公开的一个实施例，所述阀体包括形成所述内部流道的阀座和安装在该阀座上的第一阀壳和第二阀壳，所述第一阀壳内安装有用于驱动所述第一阀芯的第一电磁驱动部，所述第二阀壳内安装有用于驱动所述第二阀芯的第二电磁驱动部，所述第一阀芯从所述第一阀壳延伸至所述阀座内的所述内部流道，所述第二阀芯从所述第二阀壳延伸至所述阀座内的所述内部流道。
根据本公开的一个实施例，所述阀座形成为多面体结构，所述第一阀壳、所述第二阀壳、所述进口和所述出口分别设置在该多面体结构的不同表面上，其中，所述第一阀壳和所述第二阀壳的安装方向相互垂直，所述进口和所述出口的开口方向相互垂直。
通过上述技术方案，通过在同一阀体的内部流道上安装第一阀芯和第二阀芯，能够实现冷剂的通断控制和/或节流膨胀控制功能，结构简单，易于生产和安装，且当本公开提供的膨胀开关阀应用于热泵系统时，可以简化管路连接降低成本，并且减少整个热泵系统的制冷剂充注量，便于压缩机回油。
本公开的其他特征和优点将在随后的具体实施方式部分予以详细说明。
附图说明
附图是用来提供对本公开的进一步理解，并且构成说明书的一部分，与下面的具体实施方式一起用于解释本公开，但并不构成对本公开的限制。在附图中：
图1是本公开优选实施方式提供的膨胀开关阀的俯视结构示意图；
图2是沿图1中线AB-AB所剖得的剖面结构示意图，其中，第一阀口和第二阀口均处于打开状态；
图3是本公开优选实施方式提供的膨胀开关阀的沿一个视角的正视结构示意图；
图4是沿图1中线AB-AB所剖得的剖面结构示意图，其中，第一阀口处于打开状态，第二阀口处于闭合状态；
图5是沿图1中线AB-AB所剖得的剖面结构示意图，其中，第一阀口处于闭合状态，第二阀口处于打开状态；
图6是本公开优选实施方式提供的膨胀开关阀的沿另一个视角的正视结构示意图；
图7是沿图6中线AC-AC所剖得的剖面结构示意图，其中，第一阀口处于打开状态，第二阀口处于闭合状态；
图8是本公开优选实施方式提供的膨胀开关阀的第一内部结构示意图，其中，第一阀口和第二阀口均处于打开状态；
图9是图8中A部的局部放大图；
图10是本公开优选实施方式提供的膨胀开关阀的第二内部结构示意图，其中，第一阀口处于打开状态，第二阀口处于关闭状态；
图11是本公开优选实施方式提供的膨胀开关阀的第三内部结构示意图，其中，第一阀口处于关闭状态，第二阀口均处于打开状态。
附图标记说明
500阀体               501进口            502出口
503第一阀芯        513第一阀杆         523第一堵头
504第二阀芯        514第二阀杆         505节流口
506第一流道        516第一阀口         526第一通孔
507第二流道        517第二阀口         527第二通孔
510阀座               511第一阀壳         521第一电磁驱动部
512第二阀壳        522第二电磁驱动部
具体实施方式
以下结合附图对本公开的具体实施方式进行详细说明。应当理解的是，此处所描述的具体实施方式仅用于说明和解释本公开，并不用于限制本公开。
在本公开中，在未作相反说明的情况下，使用的方位词如“上、下、左、右”通常是相对于附图的图面方向而言的，“上游、下游”是相对于媒介，如，制冷剂的流动方向而言的，具体地，朝向制冷剂的流动方向为下游，背离制冷剂的流动方向为上游，“内、外”是指相应部件轮廓的内与外。
如图1所示，本公开提供一种膨胀开关阀，包括阀体500，其中，该阀体500上形成有进口501、出口502以及连通在进口501和出口502之间的内部流道，内部流道上安装有第一阀芯503和第二阀芯504，第一阀芯503使得进口501和出口502直接连通或断开连通，第二阀芯504使得进口501和出口502通过节流口505连通或断开连通。
其中，第一阀芯所实现的“直接连通”是指从阀体500的进口501进入的制冷剂可以越过第一阀芯而通过内部流道不受影响地直接流到阀体500的出口502，第一阀芯所实现的“断开连通”是指从阀体500的进口501进入的制冷剂无法越过第一阀芯而不能通过内部流道流向阀体500的出口502。第二阀芯所实现的“通过节流口连通”是指从阀体500的进口501进入的制冷剂可以越过第二阀芯而通过节流口的节流后流到阀体500的出口502，而第二阀芯所实现的“断开连通”是指从阀体500的进口501进入的制冷剂无法越过第二阀芯而不能通过节流口505流到阀体500的出口502。
这样，通过对第一阀芯和第二阀芯的控制，本公开的膨胀开关阀可以使得从进口501进入的制冷剂至少实现三种状态。即，1)截止状态；2)越过第一阀芯503的直接连通状态；以及3)越过第二阀芯504的节流连通方式。
其中，高温高压的液态制冷剂在经过节流口505节流后，可以成为低温低压的雾状的液态制冷剂，可以为制冷剂的蒸发创造条件，即节流口505的横截面积小于出口502的横截面积，并且通过控制第二阀芯，节流口505的开度大小可以调节，以控制流经节流口505的流量，防止因制冷剂过少产生的制冷不足，以及防止因制冷剂过多而使得压缩机产生液击现象。即，第二阀芯504和阀体500的配合可以使得膨胀开关阀具有膨胀阀的功能。
这样，通过在同一阀体500的内部流道上安装第一阀芯503和第二阀芯504，以实现进口501和出口502的通断控制和/或节流控制功能，结构简单，易于生产和安装，且当本公开提供的膨胀开关阀应用于热泵系统时，可以减少整个热泵系统的制冷剂充注量，降低成本，简化管路连接，更利于热泵系统的回油。
作为阀体500的一种示例性的内部安装结构，如图1至图6所示，阀体500包括形成内部流道的阀座510和安装在该阀座510上的第一阀壳511和第二阀壳512，第一阀壳511内安装有用于驱动第一阀芯503的第一电磁驱动部521，第二阀壳512内安装有用于驱动第二阀芯504的第二电磁驱动部522，第一阀芯503从第一阀壳511延伸至阀座510内的内部流道，第二阀芯504从靠近第二阀壳512的一端延伸至阀座510内的内部流道。
其中，通过对第一电磁驱动部521(如，电磁线圈)的通断电的控制能够方便地控制第一阀芯503的位置，进而控制进口501和出口502直接连通或断开连通；通过对第二电磁驱动部522(如，电磁线圈)的通断电的控制能够方便地控制第二阀芯504的位置，从而控制进口501和出口502是否与节流口505连通。换言之，阀体500内并联安装有共有进口501和出口502的电子膨胀阀和电磁阀，因而能够实现膨胀开关阀的通断和/或节流的自动化控制，且简化管路走向。
为充分利用膨胀开关阀的各个方向的空间位置，避免膨胀开关阀和不同管路连接产生干涉，阀座510形成为多面体结构，第一阀壳511、第二阀壳512、进口501和出口502分 别设置在该多面体结构的不同表面上，其中，第一阀壳511和第二阀壳512的安装方向相互垂直，进口501和出口502的开口方向相互垂直。这样，可以将进口、出口管路连接在多面体结构的不同表面上，能够避免管路布置凌乱、纠缠的问题。
作为电磁膨胀阀的一种典型的内部结构，如图1至图4所示，内部流道包括分别与进口501连通的第一流道506和第二流道507，第一流道506上形成有与第一阀芯503配合的第一阀口516，节流口505形成在第二流道507上以形成为与第二阀芯504配合的第二阀口517，第一流道506和第二流道507交汇于第二阀口517的下游并与出口502连通。
即，通过变换第一阀芯503的位置来实现对第一阀口516的关闭或打开，进而控制连通进口501和出口502的第一流道506的截断或导通，从而可以实现上文描述的电磁阀的连通或断开连通的功能。同样地，通过变换第二阀芯504的位置来实现对第二阀口517的截断或导通，从而可以实现电子膨胀阀的节流功能。
第一流道506和第二流道507能够以任意合适的布置方式分别连通进口501和出口502，为减少阀体500的整体占用空间，如图5所示，第二流道507与出口502同向开设，第一流道506形成为与第二流道507相互垂直的第一通孔526，进口501通过开设在第二流道507侧壁上的第二通孔527与第二流道507连通，第一通孔526和第二通孔527与进口501分别连通。其中，第一通孔526可以与第二通孔527在空间垂直设置或者平行设置，本公开对此不作限制，均属于本公开的保护范围之中。
为进一步简化阀体500的整体占用空间，如图8至图11所示，进口501与出口502相互垂直地开设在阀体500上。这样，如图8至图10所示，进口501的轴线、出口502的轴线(即第二流道507的轴线)，和第一流道506的轴线在空间两两垂直地布置，从而防止第一阀芯503和第二阀芯504的移动产生干涉，且能够最大化地利用阀体500的内部空间。
如图4和图5所示，为便于实现第一阀口516的关闭和打开，第一阀芯503沿移动方向与第一阀口516同轴布设以可选择地封堵或脱离第一阀口516。
为便于实现第二阀口517的关闭和打开，第二阀芯504沿移动方向与第二阀口517同轴布设以可选择地封堵或脱离第二阀口517。
其中，如图7所示，为保证第一阀芯503对第一流道506堵塞的可靠性，第一阀芯503可以包括第一阀杆513和连接在该第一阀杆513端部的第一堵头523，该第一堵头523用于密封压靠在第一阀口516的端面上以封堵第一流道506。
为便于调节膨胀开关阀的节流口505的开度大小，如图4和图5所示，第二阀芯504包括第二阀杆514，该第二阀杆514的端部形成为锥形头结构，第二阀口517形成为与该锥形头结构相配合的锥形孔结构。
其中，膨胀开关阀的节流口505开度可以通过第二阀芯504的上下移动来调节，而第 二阀芯504的上下移动可以通过第二电磁驱动部522来调节。若膨胀开关阀的节流口505的开度为零，如图4所示，第二阀芯504处于最低位置，第二阀芯504封堵第二阀口517，制冷剂完全不能通过节流口505，即第二阀口517；若膨胀开关阀节流口505具有开度，如图5所示，第二阀芯504的端部的锥形头结构与节流口505之间具有空隙，制冷剂节流后再流至出口502。若需要增加膨胀开关阀的节流开度时，可以通过控制第二电磁驱动部522，使得第二阀芯504向上移动，以使得锥形头结构远离节流口505，从而实现节流口505开度的变大；相反，当需要减少膨胀开关阀的节流口505的开度时，可以驱使第二阀芯504向下移动即可。
使用时，当只需要使用膨胀开关阀的电磁阀功能时，如图4、图7和图10所示，第一阀芯503脱离第一阀口516，第一阀口516处于打开状态，第二阀芯504处于最低位置，第二阀芯504将节流口505封堵上，从进口501流入至内部流道的制冷剂完全不能通过节流口505，只能依次通过第一阀口516、第一通孔526流入至出口502中。当电磁阀断电，第一阀芯503向左移动，第一堵头523和第一阀口516分离，制冷剂可以从第一通孔526中通过；当电磁阀通电，第一阀芯503向右移动，第一堵头523和第一阀口516贴合，制冷剂无法从第一通孔526中通过。
需要说明的是，图4和图10中的带箭头的虚线代表制冷剂在使用电磁阀功能时的流动路线以及走向。
当只需要使用膨胀开关阀的电子膨胀阀功能时，如图5和图11所示，第二阀口517，即节流口505处于打开状态，第一阀芯503封堵第一阀口516，从进口501流入至内部流道的制冷剂无法通过第一通孔526，只能依次通过第二通孔527、节流口505流入至出口502中，并且可以上下移动第二阀芯504来调节节流口505的开度的大小。
需要说明的是，图5和图11中的带箭头的虚线代表制冷剂在使用电子膨胀阀功能时的流动路线以及走向。
当需要同时使用膨胀开关阀的电磁阀功能和电子膨胀阀功能时，如图2、图8和图9所示，其中，带箭头的虚线代表制冷剂的流动路线以及走向，第一阀芯503脱离第一阀口516，第一阀口516处于打开状态，节流口505处于打开状态，流入至内部流道的制冷剂可以分别沿第一流道506和第二流道507流向出口502，从而同时具有电磁阀功能和电子膨胀阀功能。
以上结合附图详细描述了本公开的优选实施方式，但是，本公开并不限于上述实施方式中的具体细节，在本公开的技术构思范围内，可以对本公开的技术方案进行多种简单变型，这些简单变型均属于本公开的保护范围。
另外需要说明的是，在上述具体实施方式中所描述的各个具体技术特征，在不矛盾的 情况下，可以通过任何合适的方式进行组合，为了避免不必要的重复，本公开对各种可能的组合方式不再另行说明。
此外，本公开的各种不同的实施方式之间也可以进行任意组合，只要其不违背本公开的思想，其同样应当视为本公开所公开的内容。

Claims (10)

  1. 一种膨胀开关阀，包括阀体(500)，其特征在于，所述阀体(500)上形成有进口(501)、出口(502)以及连通在所述进口(501)和所述出口(502)之间的内部流道，所述内部流道上安装有第一阀芯(503)和第二阀芯(504)，所述第一阀芯(503)使得所述进口(501)和所述出口(502)直接连通或断开连通，所述第二阀芯(504)使得所述进口(501)和所述出口(502)通过节流口(505)连通或断开连通。
  2. 根据权利要求1所述的膨胀开关阀，其特征在于，所述内部流道包括分别与所述进口(501)连通的第一流道(506)和第二流道(507)，所述第一流道(506)上形成有与所述第一阀芯(503)配合的第一阀口(516)，所述节流口(505)形成在所述第二流道(507)上以形成为与所述第二阀芯(504)配合的第二阀口(517)，所述第一流道(506)和所述第二流道(507)交汇于所述第二阀口(517)的下游并与所述出口(502)连通。
  3. 根据权利要求2所述的膨胀开关阀，其特征在于，所述第二流道(507)与所述出口(502)同向开设，所述第一流道(506)形成为与所述第二流道(507)相互垂直的第一通孔(526)，所述进口(501)通过开设在所述第二流道(507)侧壁上的第二通孔(527)与所述第二流道(507)连通，所述第一通孔(526)和所述第二通孔(527)与所述进口(501)分别连通。
  4. 根据权利要求1-3中任意一项所述的膨胀开关阀，其特征在于，所述进口(501)与所述出口(502)相互垂直地开设在所述阀体(500)上。
  5. 根据权利要求2或3所述的膨胀开关阀，其特征在于，所述第一阀芯(503)沿移动方向与所述第一阀口(516)同轴布设以可选择地封堵或脱离所述第一阀口(516)。
  6. 根据权利要求2或3所述的膨胀开关阀，其特征在于，所述第二阀芯(504)沿移动方向与所述第二阀口(517)同轴布设以可选择地封堵或脱离所述第二阀口(517)。
  7. 根据权利要求5所述的膨胀开关阀，其特征在于，所述第一阀芯(503)包括第一阀杆(513)和连接在所述第一阀杆(513)端部的第一堵头(523)，所述第一堵头(523)用于密封压靠在所述第一阀口(516)的端面上以封堵所述第一流道(506)。
  8. 根据权利要求6所述的膨胀开关阀，其特征在于，所述第二阀芯(504)包括第二阀杆(514)，所述第二阀杆(514)的端部形成为锥形头结构，所述第二阀口(517)形成为与所述锥形头结构相配合的锥形孔结构。
  9. 根据权利要求1所述的膨胀开关阀，其特征在于，所述阀体(500)包括形成所述内部流道的阀座(510)和安装在所述阀座(510)上的第一阀壳(511)和第二阀壳(512)，所述第一阀壳(511)内安装有用于驱动所述第一阀芯(503)的第一电磁驱动部(521)， 所述第二阀壳(512)内安装有用于驱动所述第二阀芯(504)的第二电磁驱动部(522)，所述第一阀芯(503)从所述第一阀壳(511)延伸至所述阀座(510)内的所述内部流道，所述第二阀芯(504)从所述靠近第二阀壳(512)的一端延伸至所述阀座(510)内的所述内部流道。
  10. 根据权利要求9所述的膨胀开关阀，其特征在于，所述阀座(510)形成为多面体结构，所述第一阀壳(511)、所述第二阀壳(512)、所述进口(501)和所述出口(502)分别设置在所述多面体结构的不同表面上，其中，所述第一阀壳(511)和所述第二阀壳(512)的安装方向相互垂直，所述进口(501)和所述出口(502)的开口方向相互垂直。
PCT/CN2017/082946 2016-05-10 2017-05-03 膨胀开关阀 Ceased WO2017193855A1 (zh)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP17795473.2A EP3453929A4 (en) 2016-05-10 2017-05-03 RELAXATION SWITCH VALVE
US16/300,431 US20190257560A1 (en) 2016-05-10 2017-05-03 Expansion switch valve

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