WO2020039889A1 - 流路切換弁 - Google Patents

流路切換弁 Download PDF

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Publication number
WO2020039889A1
WO2020039889A1 PCT/JP2019/030394 JP2019030394W WO2020039889A1 WO 2020039889 A1 WO2020039889 A1 WO 2020039889A1 JP 2019030394 W JP2019030394 W JP 2019030394W WO 2020039889 A1 WO2020039889 A1 WO 2020039889A1
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WO
WIPO (PCT)
Prior art keywords
main valve
valve seat
flow path
valve body
path switching
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/JP2019/030394
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English (en)
French (fr)
Japanese (ja)
Inventor
木船　仁志
尚敬 藤田
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.)
Fujikoki Corp
Original Assignee
Fujikoki Corp
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 Fujikoki Corp filed Critical Fujikoki Corp
Priority to EP19851650.2A priority Critical patent/EP3842676B1/en
Priority to CN201980055106.2A priority patent/CN112585384B/zh
Publication of WO2020039889A1 publication Critical patent/WO2020039889A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/0655—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with flat slides
    • 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
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F16K31/0617—Sliding valves with flat slides
    • 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
    • F16K31/1225—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston with a plurality of pistons
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve

Definitions

  • the present invention relates to a flow path switching valve that switches a flow path by moving a valve element, and for example, relates to a flow path switching valve suitable for performing a flow path switching in a heat pump type cooling / heating system or the like.
  • a heat pump type cooling / heating system such as a room air conditioner includes a flow path switching valve (four-way switching) as flow path (flow direction) switching means in addition to a compressor, an outdoor heat exchanger, an indoor heat exchanger, an expansion valve, and the like. Valves and a six-way switching valve), and the operation mode (cooling operation and heating operation) is switched by the flow path switching valve.
  • the slide type flow path switching valve (six-way switching valve) includes three cylindrical main valve housings each defining a main valve chamber, and three main valve housings (main valve chambers) on opposite sides of the axis of the main valve housing (main valve chamber).
  • a main valve seat having a valve seat surface with an opened port, and a port movably disposed in the main valve chamber in the axial direction, and slidably contacting the valve seat surface.
  • a main valve element having a slidable main valve element, wherein the main valve element has a first U-turn passage (high-pressure U-turn passage) for selectively communicating two of the three ports.
  • a second slide valve element having a second U-turn passage (low-pressure U-turn path) for selectively communicating one slide valve element (high-pressure side slide valve element) with two of the other three ports. (Low pressure side slide valve element), and these slide valve elements are
  • the respective U-turn passages are arranged back-to-back so as to open in opposite directions, and the slide valve bodies are integrally movable in the axial direction, and are mutually movable in a direction perpendicular to the axis. It is slidable, and by moving the main valve body in the main valve chamber, the ports (flow paths) communicating with each other are switched through the U-turn passage.
  • a fluid having a high pressure relative to the first U-turn passage (high-pressure U-turn passage) of the first slide valve element (high-pressure side slide valve element) is used.
  • a relatively low-pressure fluid is introduced into a second U-turn passage (low-pressure side U-turn passage) of the second slide valve body (low-pressure side slide valve body), and a high-pressure side slide valve body and a low-pressure side slide are introduced.
  • a pressure chamber into which a part of the high-pressure fluid introduced into the high-pressure side U-turn passage is provided between the valve body and the pressure chamber in the high-pressure side slide valve body when viewed in a direction perpendicular to the axis.
  • the pressure receiving area on the side (back pressure side) is made larger than the pressure receiving area on the main valve seat side provided with three ports, that is, the opening area of the high pressure side U-turn passage of the high pressure side slide valve element.
  • the annular sealing surface of the slide valve body is formed only around the opening of the U-turn passage so that the annular shape of the slide valve body pressed against the valve seat surface of the main valve seat is formed. It is already known that the sealing performance is improved by reducing the area of the sealing surface (that is, the contact area with the valve seat surface) and increasing the pressing force (surface pressure) of the annular sealing surface against the valve seat surface. I have.
  • the annular seal surface of the slide valve body becomes main. Ports opened in the valve seat surface of the valve seat (especially edges in the axial direction (moving direction), etc.) are easily caught, and the opening of the annular sealing surface or the valve seat surface that hinders the movement of the slide valve body. There is a possibility that the sealing performance, operability, and durability may decrease due to damage or deformation of the port to be closed. Further, when the area of the annular sealing surface of the slide valve body is reduced, there is a concern that the slide valve body is likely to rattle on the valve seat surface of the main valve seat.
  • the present invention has been made in view of the above circumstances, and an object thereof is to provide a simple configuration in which an annular sealing surface of a slide valve body is caught by a port opened in a valve seat surface of a main valve seat.
  • An object of the present invention is to provide a flow path switching valve which can be prevented.
  • a flow path switching valve is basically provided with a main valve housing defining a main valve chamber, and a plurality of ports arranged in the main valve chamber and having a plurality of ports opened.
  • a first main valve seat having a closed valve seat surface, and a plurality of ports disposed in the main valve chamber on the opposite side of the first main valve seat with respect to the axis of the main valve chamber.
  • a high pressure side slide valve having a second main valve seat having a valve seat surface, a high pressure side U-turn passage through which a relatively high pressure fluid is introduced, and being slidable on the valve seat surface of the first main valve seat.
  • the pair of slide valve bodies are integrally movable in the axial direction, and are slidable with each other in a direction perpendicular to the axis.
  • a flow path switching valve configured to switch communication between the plurality of ports of each of the first main valve seat and the second main valve seat by moving a valve body;
  • the valve body has an annular sealing surface that is in contact with the valve seat surface around the opening of the high-pressure side U-turn passage in the high-pressure side sliding valve body.
  • a convex portion having the same height as the annular sealing surface is provided on the outer side in the axial direction.
  • the convex portion extends in the axial direction.
  • the convex surface is provided at least at the center in the width direction of the annular sealing surface.
  • the convex surface is provided at least on both sides in the width direction of the annular sealing surface.
  • the convex surface is provided over the entire width of the annular sealing surface.
  • the convex surface is provided continuously to the axial end of the annular sealing surface.
  • the convex surface is provided apart from the axial end of the annular sealing surface.
  • the convex surface portion is provided from the center in the width direction of the annular sealing surface in the axial direction, and extends in the axial direction from both side portions in the width direction of the annular sealing surface. It is provided away from the sealing surface.
  • the annular sealing surface is formed only at a predetermined width around the opening of the high-pressure side U-turn passage.
  • the outer shape of the pressure receiving surface of the high pressure side slide valve element on the side of the low pressure side slide valve element is set to be larger than the outer shape of the annular sealing surface.
  • annular seal member is disposed between the high-pressure side slide valve element and the low-pressure side slide valve element, and an outer shape of the seal member is set larger than an outer shape of the annular seal surface.
  • the high-pressure side slide valve body has a cylindrical shape, and a fitting protrusion that is slidably fitted to the high-pressure side slide valve body on one side surface of the low-pressure side slide valve body.
  • the fitting projection is internally fitted to the high-pressure side slide valve element, so that the high-pressure side U-turn passage is formed by the inner peripheral surface of the high-pressure side slide valve element and the end face of the fitting projection.
  • the high pressure side slide valve element and the low pressure side slide valve element are integrally movable in the axial direction and slidable with each other in a direction perpendicular to the axis.
  • the low pressure side U-turn passage is opened on the other side surface of the low pressure side slide valve body.
  • the flow path switching valve basically includes a cylindrical main valve housing defining a main valve chamber, and a valve seat surface having a plurality of ports arranged and opened in the axial direction.
  • a valve seat, and a slide-type main valve body slidably disposed in the main valve chamber so as to be movable in the axial direction and slidably contacting the valve seat surface;
  • a U-turn passage for selectively communicating between the plurality of ports is provided, and an annular seal surface that is in contact with the valve seat surface is formed around an opening of the U-turn passage.
  • the main valve body By moving the main valve body, it is a flow path switching valve that is configured to be switched between communicating ports, wherein the annular sealing surface in the axial direction outside the annular sealing surface in the main valve body, The convex part of the same height is provided It is characterized in Rukoto.
  • the convex portion having the same height as the annular seal surface is provided on the high pressure side slide valve body in the axial direction outside of the annular seal surface, the high pressure side slide valve is provided by the convex portion.
  • the annular sealing surface of the body can easily pass over the port opened in the valve seat surface of the main valve seat, and the annular sealing surface of the high pressure side slide valve body can be effectively prevented from being caught by the port, and the valve of the main valve seat can be effectively prevented. Since the backlash of the high-pressure side slide valve element on the seat surface can be reduced, the sealability, operability, durability, stability, and the like can be effectively improved.
  • the convex portion is provided at least on both sides in the width direction of the annular seal surface, for example, even when the high pressure side slide valve body slides on the valve seat surface of the main valve seat in a tilted state, the high pressure side Before the (one side of) the annular seal surface of the slide valve element contacts the valve seat surface of the main valve seat, the convex portion contacts the valve seat surface of the main valve seat, so that durability is reliably improved. Can be done.
  • the convex portion is provided over the entire width direction of the annular sealing surface, the convex portion allows the annular sealing surface of the high-pressure side slide valve body to be opened to the valve seat surface of the main valve seat. It is easy to get over reliably, and it is possible to more effectively prevent the annular seal surface of the high pressure side slide valve body from catching on the port, and to further reduce the backlash of the high pressure side slide valve body on the valve seat surface of the main valve seat. can do.
  • the convex portion is provided continuously to the axial end portion of the annular seal surface, it is possible to more reliably prevent the annular seal surface of the high pressure side slide valve body from being caught by the port, and to prevent the valve of the main valve seat from being caught.
  • the rattling of the high pressure side slide valve body on the seat surface can be reduced more reliably.
  • the convex portion is provided apart from the axial end of the annular seal surface, the pressure (surface pressure) distribution on the annular seal surface of the high-pressure side slide valve body can be easily controlled, and the sealing performance and operability are improved. , Durability, stability, etc. can be effectively improved, and the groove formed between the annular sealing surface and the convex portion functions as a foreign matter discharge passage. Foreign matter accumulation can also be effectively prevented.
  • FIG. 3 is a longitudinal sectional view showing a first communication state (at the time of cooling operation) of the first embodiment of the flow path switching valve according to the present invention.
  • FIG. 4 is a longitudinal sectional view showing a second communication state (at the time of a heating operation) of the first embodiment of the flow path switching valve according to the present invention.
  • FIG. 2 is an enlarged vertical cross-sectional view of a main part of the flow path switching valve shown in FIG. 1.
  • FIG. 5 is a sectional view taken along line VV of FIG. 3.
  • FIG. 4 is a sectional view taken along line WW of FIG. 3.
  • FIG. 2 is a sectional view taken along the line UU in FIG. 1.
  • FIG. 1 is a longitudinal sectional view showing a first communication state (at the time of cooling operation) of the first embodiment of the flow path switching valve according to the present invention.
  • FIG. 4 is a longitudinal sectional view showing a second communication state (at the time of a heating operation) of the first embodiment of the flow path switching
  • FIG. 2 is a perspective view showing a main valve body and a connection body of the first embodiment of the flow path switching valve according to the present invention.
  • FIG. 4 is an enlarged longitudinal sectional view showing a first communication state (at the time of cooling operation) (at the time of energization OFF) of the four-way pilot valve used in the flow path switching valve according to the present invention.
  • FIG. 4 is an enlarged longitudinal sectional view showing a second communication state (at the time of heating operation) (at the time of energization ON) of the four-way pilot valve used in the flow path switching valve according to the present invention.
  • FIG. 4 is a cross-sectional view of a flow path switching valve according to a second embodiment of the present invention, taken along line WW of FIG. 3.
  • FIG. 4 is a sectional view of a third embodiment of the flow path switching valve according to the present invention, taken along line WW of FIG. 3.
  • FIG. 9 is a perspective view showing a main valve body and a connection body of a third embodiment of the flow path switching valve according to the present invention.
  • FIG. 4 is a cross-sectional view of a fourth embodiment of a flow path switching valve according to the present invention, taken along line WW of FIG. 3.
  • FIG. 13 is a perspective view showing a main valve body and a connecting body of a fourth embodiment of the flow path switching valve according to the present invention.
  • FIG. 14 is a sectional view of a fifth embodiment of the flow path switching valve according to the present invention, taken along line WW of FIG. 3.
  • the perspective view which shows the main valve body and connection body of 5th Embodiment of the flow-path switching valve which concerns on this invention.
  • FIG. 1 and 2 are longitudinal sectional views showing a first embodiment of a flow path switching valve (a six-way switching valve) according to the present invention.
  • FIG. 1 shows a first communication state (at the time of cooling operation)
  • FIG. 8 is a diagram showing a second communication state (during a heating operation).
  • a gap formed between members, a separation distance between members, and the like are larger than dimensions of each constituent member for easy understanding of the invention and for convenience of drawing. Or it may be drawn small.
  • the flow path switching valve 1 of the illustrated embodiment is, for example, a slide type used as a six-way switching valve in a heat pump type cooling / heating system, and basically includes a cylinder type six-way valve body 10 and a single electromagnetic valve as a pilot valve. And a four-way pilot valve 90.
  • the six ports provided in the flow path switching valve 1 of the present embodiment are assigned the same reference numerals corresponding to the respective ports pA to pF of the six-way switching valve described in Patent Documents 1 and 2. Have been.
  • the six-way valve main body 10 has a cylindrical main valve housing 11 made of metal such as brass or stainless steel, and the main valve housing 11 is provided with a first working chamber 31 and a first working chamber 31 in order from one end side (upper end side).
  • a first piston 21, a main valve chamber 12, a second piston 22, and a second working chamber 32 are arranged.
  • Each of the first and second pistons 21 and 22 is provided with a spring-loaded packing whose outer peripheral portion is pressed against the inner peripheral surface of the main valve housing 11 in order to partition the main valve housing 11 in an airtight manner. .
  • the main valve housing 11 has a body portion 11c having a relatively large diameter, and is provided on a thick disk-shaped upper connection lid 11d that is hermetically attached to an upper end opening of the body portion 11c.
  • a first piston portion 11a made of a pipe member (having a relatively small diameter) is air-tightly fixed to the central hole by brazing or the like, and the first piston 21 is arranged in the first piston portion 11a.
  • a second piston portion made of a pipe member (having a relatively small diameter) is provided in a center hole provided in a thick disc-shaped lower connection lid 11e which is hermetically attached to a lower end opening of the body portion 11c.
  • 11b is hermetically fixed by brazing or the like, and the second piston 22 is disposed on the second piston portion 11b.
  • a thin disk-shaped upper end side lid member 11A defining a first working chamber 31 having a variable capacity is hermetically fixed by brazing or the like.
  • a thin disk-shaped lower end side lid member 11B defining a variable capacity second working chamber 32 is hermetically fixed by brazing or the like.
  • Ports p11 and p12 for introducing and discharging a high-pressure fluid (refrigerant) into and from the first working chamber 31 and the second working chamber 32 are attached to (the center of) the upper end side lid member 11A and the lower end side lid member 11B, respectively. ing.
  • a first main valve seat (valve seat) 13 made of, for example, metal whose surface (right surface) is a flat valve seat surface is formed by brazing or the like. It is airtightly fixed to (the inner periphery of) the body 11c of the housing 11.
  • three ports (port pB, port pA, port pF) formed of a pipe joint extending leftward are arranged vertically (in the direction of the axis O). The openings are arranged at substantially equal intervals.
  • the right side center (the position facing the first main valve seat 13, in other words, the position on the opposite side of the first main valve seat 13 with respect to the axis O) of the main valve chamber 12 has its surface (left surface).
  • a second main valve seat (valve seat) 14 made of metal is hermetically fixed to (the inner periphery of) the body 11c of the main valve housing 11 by brazing or the like.
  • three ports (ports pC, port pD, and port pE) consisting of pipe joints extending rightward are arranged vertically (in the direction of the axis O). The openings are arranged at substantially equal intervals.
  • the ports pA to pF provided in the first main valve seat 13 and the second main valve seat 14 are set to have substantially the same diameter. Have been.
  • both side surfaces are valve seat surfaces of the first main valve seat 13 and the second main valve seat 14.
  • the dimensions of the main valve body 15 in the left-right direction and the front-rear direction are equal to or slightly larger than the outer diameters of the first piston portion 11a and the second piston portion 11b of the main valve housing 11.
  • the main valve body 15 is made of, for example, a synthetic resin, and basically includes a first slide valve body (high-pressure side slide valve body) 15A on the first main valve seat 13 side (left side) and a second main valve seat 14. And a second slide valve body (low pressure side slide valve body) 15B on the side (right side).
  • the first slide valve body 15A has a substantially cylindrical shape, and is opened on the valve seat surface of the first main valve seat 13 on the inner periphery of the left end (the end opposite to the second slide valve body 15B).
  • Inner flange portion 15a defining an opening large enough to selectively communicate two adjacent ports (port pB and port pA or port pA and port pF) among the three ports. Is protruding (inward).
  • the left end surface (the end surface on the first main valve seat 13 side) of the inner flange portion 15a is the annular sealing surface 15s which is slidably brought into contact with the valve seat surface of the first main valve seat 13. I have.
  • the annular seal surface 15s provided on the left side (the first main valve seat 13 side) of the (first inner valve-like portion 15a) of the first slide valve body 15A (to be described later). It is formed only at a predetermined width (approximately the same width over the entire circumference) around the opening of the 1U-turn passage (high-pressure U-turn passage) 16A (particularly, see FIGS. 5 to 7).
  • the upper and lower ends (in other words, both ends in the direction of the axis O or the moving direction) of the annular sealing surface 15s are in the width direction (the front-rear direction in the illustrated example, perpendicular to the axis O, and At the center of the first and second main valve seats 13 and 14 (in a direction parallel to the valve seat surfaces), the same height as the annular sealing surface 15s is provided in the vertical direction (along the direction of the axis O). Further, a substantially bar-shaped convex portion 15t narrower than (the outer shape of) the annular sealing surface 15s is continuously provided (continuously extended) (in particular, see FIGS. 5 to 7). In the illustrated example, the width of the substantially bar-shaped convex surface portion 15t is substantially the same as the width (the predetermined width) of the race track-shaped annular sealing surface 15s formed around the opening of the first U-turn passage 16A.
  • the contact area between the first slide valve element 15A (the annular sealing surface 15s) and the first main valve seat 13 (the valve seat surface) becomes small, and the first main valve seat 13 has the first contact surface with respect to the valve seat surface.
  • the pressing force (surface pressure) of the annular seal surface 15s on the left side of the slide valve body 15A increases, and the first slide valve body 15A slides on the valve seat surface of the first main valve seat 13 during flow path switching.
  • the annular seal surface 15s of the first slide valve body 15A is less likely to be caught by a port opened on the valve seat surface of the first main valve seat 13.
  • a second U-turn passage (low-pressure-side U-turn passage) 16B is formed of a bowl-shaped recess having a size such that the ports (ports pC and pD or ports pD and port pE) can be selectively communicated.
  • a fitting having an outer shape that is substantially the same as or slightly smaller than the inner shape of the cylindrical first slide valve body 15A is fitted on the left surface (side surface on the side of the first slide valve body 15A) of the second slide valve body 15B.
  • the mating projection 15b extends (to the left).
  • the fitting projection 15b of the second slide valve element 15B is slidably slidable (on the right side of the cylindrical first slide valve element 15A) (with the O-ring 18 interposed between the step portions provided therebetween).
  • the inner peripheral surface of the first slide valve body 15A and the left end surface of the fitting convex portion 15b are adjacent to one of the three ports opened on the valve seat surface of the first main valve seat 13.
  • a first U-turn passage (high-pressure-side U-turn passage) 16A for selectively communicating two matching ports (port pB and port pA or port pA and port pF) and a first slide valve are provided.
  • the body 15 ⁇ / b> A and the second slide valve body 15 ⁇ / b> B are connected to each other (ports (port pB, port pA, port pF) provided in the first main valve seat 13 in a left-right direction (a direction perpendicular to the axis O).
  • Port pC, port pD, and port pE) are slightly movable relative to each other in the direction in which they face each other (ie, the direction orthogonal to the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14), and , And can be moved integrally in the vertical direction (the direction of the axis O).
  • the main valve body 15 is a first U-turn that can selectively communicate two adjacent ports among the three ports opened on the valve seat surface of the first main valve seat 13.
  • a second U-turn passage 16B capable of selectively communicating adjacent two of the three ports opened in the valve seat surface of the first slide valve element 15A having the passage 16A and the second main valve seat 14 is provided.
  • a pair of first and second slide valve bodies 15A and 15B, the first and second U-turn passages 16A and 16B open in opposite directions. As described above (in other words, in a direction orthogonal to the valve seat surfaces of the first and second main valve seats 13 and 14), they are arranged back to back.
  • a step portion inner peripheral step portion formed on the inner periphery on the right end side of the first slide valve body 15A and a step portion (outer periphery) formed on the outer periphery of the fitting projection 15b of the second slide valve body 15B.
  • An O-ring 18 as an annular sealing member is interposed between the O-ring 18 and the step portion.
  • a seal member such as a lip seal may be used instead of the O-ring 18.
  • first slide valve body 15A inside the O-ring 18 and on the first main valve seat 13 side receives high-pressure fluid (refrigerant) from the port (discharge-side high-pressure port) pA via the first U-turn passage 16A.
  • first U-turn passage 16A and the main valve chamber 12 are sealed (sealed) by the O-ring 18 disposed therebetween.
  • FIGS. 3 to 5 when viewed in the left-right direction (the direction perpendicular to the axis O), the right side (first side) of the first slide valve body 15A
  • the pressure receiving area Sc on the two-slide valve body 15B side (back pressure side) is made larger than the pressure receiving area Sa on the left side (first main valve seat 13 side).
  • Is the projected area of the surface receiving pressure in the left direction is the projected area of the inner edge of the annular sealing surface 15s on the first main valve seat 13 side with respect to a plane perpendicular to the left-right direction (that is, in this case, (The area approximately equal to the projected area of the inner flange portion 15a), and the surface of the first slide valve body 15A (left surface) which receives the rightward pressure by the high-pressure refrigerant flowing through the port (inside the annular sealing surface 15s). It is larger than the projection area (pressure receiving area Sa).
  • the pressure (more specifically, the first U-pressure) received from (the high-pressure refrigerant of) the first U-turn passage 16A Due to the pressure difference between the pressure received from the refrigerant (high-pressure refrigerant) flowing through the turn passage 16A and the pressure received from the refrigerant (low-pressure refrigerant) flowing through the second U-turn passage 16B (the annular sealing surface of the right surface of the second slide valve body 15B).
  • the right side (the second slide valve body 15B side) of the first slide valve body 15A when viewed in the left-right direction (the direction perpendicular to the axis O), the right side (the second slide valve body 15B side) of the first slide valve body 15A
  • the outer shape of the pressure receiving area Sc on the pressure side (that is, the outer shape of the O-ring 18) is larger than the outer shape of the contact area Sb of the annular sealing surface 15s and the convex surface portion 15t on the left side (the first main valve seat 13 side) (over the entire circumference). ) Will be enlarged.
  • the outer shape of the pressure receiving area Sc on the right side of the first slide valve element 15A (that is, the outer shape of the O-ring 18) is set outside the annular seal surface 15s and the convex surface portion 15t.
  • the pressing force (surface pressure) of the left surface (the annular sealing surface 15s) of the first slide valve body 15A against the valve seat surface of the first main valve seat 13 is substantially uniform.
  • first slide valve body 15A and the second slide valve body 15B for example, a step surface (leftward facing) that forms the fitting projection 15b of the right side of the first slide valve body 15A and the second slide valve body 15B.
  • a biasing member (ring-shaped leaf spring, compression coil spring, etc.) for biasing the first slide valve body 15A and the second slide valve body 15B in mutually opposite directions (directions of separation) between the first slide valve body 15A and the second slide valve body 15B.
  • the annular seal surface may be pressed (pressed) against the valve seat surface of the second main valve seat 14.
  • the main valve element 15 is configured such that the first slide valve element 15A and the second slide valve element 15B are integrally moved in the direction of the axis O, and a port pF as shown in FIG.
  • the port pB is opened and the port pB is connected to the port pA via the first U-turn passage 16A of the first slide valve body 15A, and the port pE is opened and the port pC and the port pD are connected to the second U-turn of the second slide valve body 15B.
  • a cooling position (upper end position) communicating through the passage 16B and a port pB as shown in FIG.
  • FIG. 2 opening the port pA and the port pF through the first U-turn passage 16A of the first slide valve body 15A, as shown in FIG.
  • Is adapted can take selectively a location).
  • the first slide valve body 15A of the main valve body 15 is located immediately above two of the three ports (port pB and port pA or port pA and port pF) except during movement.
  • the second slide valve body 15B of the main valve body 15 is located immediately above two of the three ports (port pC and port pD or port pD and port pE) except during movement.
  • the pressure from the high-pressure refrigerant introduced into (the first U-turn passage 16A of) the main valve body 15 is pressed left and right, respectively, and the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14 are formed. It is pressed against.
  • the first piston 21 and the second piston 22 are connected by a connecting body 25 so as to be integrally movable.
  • the connecting body 25 is connected to a first slide valve body 15A and a second slide valve body 15B of the main valve body 15. Are fitted and supported in a state where they are slightly slidable in the left-right direction and substantially prevented from moving in the front-rear direction.
  • the connecting body 25 is formed of a pair of plate members having the same size and the same shape, which are manufactured by, for example, press molding, and the respective plate members are arranged in the left-right direction (the first main valve seat 13 and the second Along the direction perpendicular to the valve seat surface of the main valve seat 14 (in other words, so as to be parallel to a plane perpendicular to the valve seat surface), and the pair of plate members
  • the main valve body 15 is sandwiched (in the front-rear direction) between the pair of plate members.
  • the plate member disposed on the front side of the main valve body 15 is referred to as a connection plate 25A
  • the plate member disposed on the rear side of the main valve body 15 is referred to as a connection plate 25B.
  • each of the connecting plates 25A and 25B is symmetric with respect to a center line (a line of symmetry) extending in the front-rear direction from the center. It is composed of a vertically elongated rectangular plate (here, the same width over the entire vertical length).
  • the main valve body 15 (the front part or the rear part) is engaged and supported integrally and movably in the direction of the axis O.
  • a support plate portion 25c is formed along the outer periphery (front and upper and lower surfaces, or rear and upper and lower surfaces) of the valve body 15 (that is, a substantially concave cross section).
  • connection plate 25a extending up to the first piston 21 or the second piston 22 is connected above and below the support plate 25c in each of the connection plates 25A and 25B.
  • the connection plate portion 25a is formed in a step shape or a crank shape by bending or the like, and has an offset plate portion 25aa and a contact plate portion 25ab from the support plate portion 25c side.
  • the offset plate portion 25aa of the connection plate portion 25a in the front connection plate 25A is opened on the valve seat surface of the first main valve seat 13 and the second main valve seat 14 in front of the axis O, particularly when viewed in the left-right direction.
  • the six ports pA to pF are arranged at positions avoiding the front side (in other words, positions offset forward from the six ports pA to pF).
  • the offset plate portion 25aa of the connection plate portion 25a in the rear connection plate 25B is opened on the valve seat surface of the first main valve seat 13 and the second main valve seat 14 behind the axis O, particularly when viewed in the left-right direction.
  • the six ports pA to pF are disposed at positions avoiding the rear side (in other words, positions offset backward from the six ports pA to pF).
  • the offset plate portions 25aa of the connection plate portions 25a of the pair of connection plates 25A and 25B are opened on the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14.
  • the ports pA to pF are arranged at a distance (in the front-rear direction) from the apertures of the squeezed ports pA to pF, and between the offset plate portions 25aa of the connection plate portions 25a in the pair of connection plates 25A and 25B. More specifically, the ports pF and pE located on the lower side in the cooling position (upper end position) shown in FIG. 1 and the ports pB and pC located on the upper side in the heating position (lower end position) shown in FIG. It will be located (especially, see FIG. 6).
  • connection plate portion 25ab of the connection plate portion 25a in the connection plates 25A and 25B (the portion close to the first piston 21 or the second piston 22 and the first main valve seat 13 and the second main valve seat 14) Portions that do not overlap with the ports pA to pF that are opened on the valve seat surface are brought into contact with the contact plate portion 25ab of the connection plate portion 25a of the connection plates 25B and 25A on the opposite side (disposed). ing.
  • unevenness or the like may be provided on the contacting plate portion 25ab in order to mutually position the connecting plates 25A and 25B arranged opposite to each other. .
  • connection plates 25A and 25B are opposite to the connection plates 25B and 25A that are opposed to each other (the direction in which the support plate portion 25c having a substantially concave cross section is formed).
  • the mounting leg portion 25b is formed by being bent at approximately 90 degrees toward.
  • a screw hole 29 for inserting a bolt 30 for connecting the connecting plate 25A, 25B to the first piston 21 or the second piston 22 is formed through the mounting leg 25b.
  • connection plate 25a offset plate 25aa + contact plate 25ab of the connection plates 25A and 25B in the up-down direction (the direction of the axis O) is the first of the main valve housing 11 and The length is shorter than the length of the second piston portions 11a and 11b.
  • the upper connection lid 11d of the main valve housing 11 (the outer peripheral portion of the first piston portion 11a) is attached to the (upper end side corner portion) of the support plate portion 25c of the connection body 25 (the respective connection plates 25A and 25B).
  • the stopper serves as a stopper that abuts and prevents the connecting body 25 (that is, the main valve body 15 fitted to the connecting body 25) from moving upward.
  • connection lid 11e (the outer peripheral portion of the second piston portion 11b) of the main valve housing 11 is attached to (the lower end side corner of) the support plate portion 25c of the connection body 25 (the respective connection plates 25A, 25B).
  • the stopper serves as a stopper that abuts and prevents the connecting body 25 (that is, the main valve body 15 fitted to the connecting body 25) from moving downward.
  • the connecting member 25 (the supporting plate portion 25c of each of the connecting plates 25A and 25B thereof) abuts on the upper connecting lid 11d or the lower connecting lid 11e of the main valve housing 11 and the main valve body 15 A stopper 25s for regulating movement in the vertical direction is provided.
  • the stopper 25s that regulates the movement of the main valve body 15 is provided in the connecting body 25, so that, for example, the upper end side lid member 11A and the lower end side lid member 11B move upward of the first piston 21.
  • the load applied to the first and second pistons 21 and 22 can be reduced, and the position of the main valve body 15 is restricted.
  • the dimensional accuracy of the components of the first and second pistons 21 and 22 and the upper and lower lid members 11A and 11B can be reduced.
  • the stopper may also serve as a stopper for preventing movement).
  • each of the connecting plates 25A and 25B is made of a plate material having the same size and the same shape, the two connecting plates 25A and 25B are arranged facing each other in the front-rear direction,
  • the connecting plate portions 25ab of the connecting plate portions 25a of the two connecting plates 25A and 25B are arranged in a reverse direction (specifically, upside down) so as to abut each other, and are mounted via bolts 30.
  • the leg 25b is fixed to the first piston 21 or the second piston 22.
  • first slide valve body 15A and the second slide valve body 15B of the main valve body 15 are inserted between the support plate portions 25c of each of the connection plates 25A and 25B (a substantially rectangular space in a side view) (in the left-right direction, respectively). ), The first slide valve element 15A and the second slide valve element 15B of the main valve element 15 are slightly slidable in the left-right direction and substantially prevented from moving in the front-rear direction.
  • the connection member 25 is fitted (particularly, see FIG. 7).
  • the main valve body 15 fitted and supported by (the pair of connecting plates 25A, 25B) of the connecting body 25 is connected to the connecting plate 25A of the connecting body 25 by the reciprocating movement of the first and second pistons 21,22. , 25B (in this case, the first sliding valve body 15A of the main valve body 15 and the second sliding valve body 15A of the main valve body 15).
  • the upper and lower surfaces of the slide valve body 15B are pressed so as to move between a cooling position (upper end position) and a heating position (lower end position).
  • connection plates 25A and 25B connection plates 25A and 25B having the same size and the same shape.
  • the main valve body 15 disposed in the main valve housing 11 When the main valve body 15 disposed in the main valve housing 11 is in the heating position (lower end position) (the second communication state as shown in FIG. 2), the main valve body 15 is connected via a four-way pilot valve 90 to be described later.
  • the second working chamber 32 When the second working chamber 32 is connected to the port pA, which is a discharge-side high-pressure port, and the first working chamber 31 is connected to a port pD, which is a suction-side low-pressure port, high-pressure refrigerant is introduced into the second working chamber 32. At the same time, high-pressure refrigerant is discharged from the first working chamber 31.
  • the pressure of the second working chamber 32 on the other end side (lower end side) of the main valve chamber 12 becomes higher than the pressure of the first working chamber 31 on one end side (upper end side) of the main valve chamber 12, as shown in FIG.
  • the first and second pistons 21 and 22 and the main valve body 15 move upward, and the stopper 25s of the connecting body 25 (the supporting plate 25c of each of the connecting plates 25A and 25B) is moved to the upper connecting lid 11d.
  • the main valve body 15 takes a cooling position (upper end position) (a first communication state as shown in FIG. 1).
  • the port pA and the port pB are communicated (via the first U-turn passage 16A), the port pC and the port pD are communicated (via the second U-turn passage 16B), and the port pE and the port pF are communicated.
  • the port pA and the port pB are communicated (via the first U-turn passage 16A)
  • the port pC and the port pD are communicated (via the second U-turn passage 16B)
  • the port pE and the port pF are communicated.
  • the first working chamber 31 is connected to the discharge-side high-pressure port via a four-way pilot valve 90 described later.
  • the second working chamber 32 is connected to a port pD which is a suction-side low-pressure port while communicating with a certain port pA, high-pressure refrigerant is introduced into the first working chamber 31 and high-pressure refrigerant is supplied from the second working chamber 32. Refrigerant is discharged. Therefore, the pressure in the first working chamber 31 at one end (upper end) of the main valve chamber 12 becomes higher than the pressure in the second working chamber 32 at the other end (lower end) of the main valve chamber 12, as shown in FIG.
  • the first and second pistons 21 and 22 and the main valve body 15 move downward, and the stopper 25s of the connecting body 25 (the supporting plate 25c of each of the connecting plates 25A and 25B) is moved to the lower connecting lid. 11e, the main valve body 15 is in the heating position (lower end position) (the second communication state as shown in FIG. 2).
  • the port pA and the port pF are communicated (via the first U-turn passage 16A), the port pE and the port pD are communicated (via the second U-turn passage 16B), and the port pC and the port pB are communicated.
  • the port pA and the port pF are communicated (via the first U-turn passage 16A)
  • the port pE and the port pD are communicated (via the second U-turn passage 16B)
  • the port pC and the port pB are communicated.
  • the structure of the four-way pilot valve 90 as a pilot valve is well known, and an electromagnetic coil 91 is fitted around the outer periphery of the base end (left end) as shown in an enlarged view in FIGS. 8A and 8B.
  • the valve case 92 includes a fixed cylindrical straight pipe, and a suction element 95, a compression coil spring 96, and a plunger 97 are arranged in series on the valve case 92 from the base end side.
  • the left end of the valve case 92 is hermetically joined by welding or the like to a flange portion (outer peripheral step portion) of the suction element 95.
  • the suction element 95 is attached to a cover case 91A that covers the outer circumference of the electromagnetic coil 91 for energizing and energizing. It is fastened and fixed by bolts 92B.
  • a lid member 98 with a filter having a thin tube insertion port (high pressure introduction port a) for introducing high pressure refrigerant is hermetically attached by welding, brazing, caulking or the like.
  • a region surrounded by the lid member 98, the plunger 97, and the valve case 92 is a valve chamber 99.
  • a high-pressure refrigerant is introduced into the valve chamber 99 from the port (discharge-side high-pressure port) pA via a high-pressure thin tube #a air-tightly inserted into a thin-tube insertion port (high-pressure introduction port a) of the lid member 98. It is supposed to be.
  • valve seat 93 whose inner end surface is a flat valve seat surface is hermetically joined by brazing or the like.
  • a port b On the valve seat surface (inner end surface) of the valve seat 93, a port connected to the first working chamber 31 of the above-described six-way valve main body 10 via the thin tube #b in order from the front end side (right end side).
  • Port c connected to pD via thin tube #c and port d connected to second working chamber 32 via thin tube #d extend in the longitudinal direction (left-right direction) of valve case 92. They are opened side by side at predetermined intervals.
  • the plunger 97 opposed to the suction element 95 is basically cylindrical, and is slidably disposed in the valve case 92 in the axial direction (along the center line L of the valve case 92). .
  • a valve body holder 94A for holding the valve body 94 slidably in the thickness direction at its free end side has its base end together with the fixture 94B. It is attached and fixed by press fitting, caulking, or the like.
  • a leaf spring 94C for urging the valve body 94 in a direction (thickness direction) of pressing the valve body 94 against the valve seat 93 is attached to the valve body holder 94A.
  • the valve body 94 is brought into contact with the valve seat surface of the valve seat 93 so as to switch the communication state between the ports b, c, and d that open to the valve seat surface of the valve seat 93.
  • the valve seat slides along with the movement of the plunger 97 in the left-right direction.
  • valve element 94 has such a size that it can selectively communicate between the adjacent ports bc and cd between the three ports b to d opening on the valve seat surface of the valve seat 93.
  • a concave portion 94a is provided.
  • the compression coil spring 96 is compressed between the suction element 95 and the plunger 97 to urge the plunger 97 away from the suction element 95 (to the right in the drawing).
  • the valve seat 93 is a stopper that prevents the plunger 97 from moving to the right. Needless to say, other configurations can be adopted as the configuration of the stopper.
  • the four-way pilot valve 90 is attached to an appropriate location such as the back side of the six-way valve main body 10 via a fixture 92A. Further, in the four-way pilot valve 90, the thin tube #c is connected to the port pD which is the suction side low pressure port, but the thin tube #c may be connected to the port pC through which the medium-pressure refrigerant flows.
  • the high-pressure fluid flowing into the port (discharge-side high-pressure port) pA is introduced into the second working chamber 32 through the high-pressure thin tube # a ⁇ the valve chamber 99 ⁇ port d ⁇ the thin tube # d ⁇ port p12, and The high-pressure fluid in the working chamber 31 flows to the port p11 ⁇ the thin tube # b ⁇ the port b ⁇ the concave portion 94a ⁇ the port c ⁇ the thin tube # c ⁇ the port (suction side low pressure port) pD and is discharged.
  • the plunger 97 is pulled by the suction force of the suction element 95 to a position where its left end contacts the suction element 95 (compression), as shown in FIGS. It is drawn (against the biasing force of the coil spring 96).
  • the valve body 94 is located above the port c and the port d, and the port c and the port d communicate with each other through the concave portion 94a, and the port b and the valve chamber 99 communicate with each other.
  • the high-pressure fluid flowing into the port (discharge-side high-pressure port) pA is introduced into the first working chamber 31 via the high-pressure capillary # a ⁇ the valve chamber 99 ⁇ port b ⁇ the capillary # b ⁇ port p11, and the second The high-pressure fluid in the working chamber 32 flows to the port p12 ⁇ the thin tube # d ⁇ the port d ⁇ the concave portion 94a ⁇ the port c ⁇ the thin tube # c ⁇ the port (suction side low pressure port) pD and is discharged.
  • the main valve body 15 of the six-way valve body 10 shifts from the heating position (the second communication state) to the cooling position (the first communication state), and the flow path as described above. While the switching is performed, when the energization to the electromagnetic coil 91 is turned ON, the main valve body 15 of the six-way valve body 10 shifts from the cooling position (the first communication state) to the heating position (the second communication state), as described above. Such flow path switching is performed.
  • the high-pressure fluid flowing through the six-way switching valve 1 (the port pA which is a high-pressure portion) is switched by turning ON / OFF the energization of the electromagnetic four-way pilot valve 90.
  • the main valve body 15 that constitutes the six-way valve body 10 is moved in the main valve chamber 12 by utilizing a pressure difference between a flowing fluid and a low-pressure fluid (fluid flowing through the port pD, which is a low-pressure portion).
  • the communication state between a total of six ports provided in the housing 11 is switched, and in the heat pump cooling and heating system, switching from heating operation to cooling operation and switching from cooling operation to heating operation can be performed.
  • the outer side of the annular sealing surface 15s in the first slide valve element (high-pressure side slide valve element) 15A in the axis O direction. Is provided with a convex surface portion 15t having the same height as the annular seal surface 15s, and the convex seal portion 15t causes the annular seal surface 15s of the first slide valve element (high-pressure side slide valve element) 15A to become the first main valve seat.
  • the annular sealing surface 15s provided on the left side (the first main valve seat 13 side) of the first slide valve body 15A is formed only at a predetermined width around the opening of the first U-turn passage 16A. Therefore, the contact area between the first sliding valve element 15A (the annular sealing surface 15s) and the first main valve seat 13 (the valve seat surface) becomes small, and the first main valve seat 13 (the valve seat surface).
  • the pressing force (surface pressure) of the first slide valve body 15A (the annular seal surface 15s thereof) against the first slide valve body 15A increases, and the sealing performance can be further improved.
  • the pressure receiving area Sc on the right side of the first slide valve body 15A can be reduced, so that the size can be reduced and the degree of freedom in arranging other assembly parts can be increased.
  • the convex surface portion 15t provided on the left side (the first main valve seat 13 side) of the first slide valve body 15A is continuous with the end of the annular seal surface 15s in the axis O direction. Since it is provided, the annular seal surface 15s of the first slide valve body (high-pressure side slide valve body) 15A can be more reliably prevented from being caught by the port, and the first slide of the first main valve seat 13 on the valve seat surface can be prevented. The rattling of the valve element (high-pressure side slide valve element) 15A can be reduced more reliably.
  • the external shape of the pressure receiving surface (pressure receiving area Sc) on the 15B side (back pressure side) (that is, the external shape of the O-ring 18) is set to be larger than the external shape of (the contact area Sb of) the annular seal surface 15s of the first slide valve body 15A.
  • the entire convex surface portion 15t connected to the annular seal surface 15s is provided so as to be located inside the pressure receiving area Sc on the right side). Since the pressure distribution on the contact surface (annular seal surface 15s) of the first slide valve body 15A becomes substantially uniform, good sealing performance, operability and stability can be ensured, and valve leakage can be effectively suppressed. .
  • FIG. 9 shows a second embodiment of a flow path switching valve (a six-way switching valve) according to the present invention.
  • the flow path switching valve 2 of the second embodiment is substantially the same as the flow path switching valve 1 of the first embodiment except for the main valve body. Therefore, the portions corresponding to the respective portions of the flow path switching valve 1 of the first embodiment and the portions having the same functions are denoted by the same reference numerals, and the description thereof will not be repeated. In the following, differences around the main valve body will be described. The explanation will focus on the points.
  • the outer shape of the pressure receiving area Sc on the right side of the first slide valve body 15A (that is, the outer shape of the O-ring 18). ) Is a race track shape, and a part of the outer shape of the pressure receiving area Sc is made smaller than the tip of the convex portion 15t on the left side.
  • the root portion (the portion adjacent to the annular seal surface 15s) of the convex portion 15t connected to the annular seal surface 15s is located inside the pressure receiving area Sc on the right side, and the tip portion (the annular portion) of the convex portion 15t. The portion separated from the sealing surface 15s) is provided outside the pressure receiving area Sc on the right side.
  • the same operation and effect as those of the flow path switching valve 1 of the first embodiment can be obtained.
  • the shape of the O-ring 18 disposed between the first slide valve body 15A and the second slide valve body 15B (sliding surface gap) can be simplified, and the annular seal surface 15s and the convex portion having pressure distribution can be simplified. Since the root portion of the 15t is effectively pressed against the valve seat surface of the first main valve seat 13, the sealing performance and the like can be further improved.
  • FIG. 10 and 11 show a third embodiment of the flow path switching valve (six-way switching valve) according to the present invention.
  • the passage switching valve 3 of the third embodiment is substantially the same as the passage switching valve 2 of the second embodiment except for the main valve body. Therefore, the portions corresponding to the respective portions of the flow path switching valve 2 of the second embodiment and the portions having the same function are denoted by the same reference numerals, and the description thereof will not be repeated. In the following, differences around the main valve body will be described. The explanation will focus on the points.
  • the annular seal surface 15s is provided above and below the annular seal surface 15s provided on the left side (the first main valve seat 13 side) of the first slide valve body 15A. (In other words, at an end in the direction of the axis O in the direction of the axis O) (that is, with a predetermined gap), a relatively large area having the same height as the annular sealing surface 15s and the same width as (the outer shape of) the annular sealing surface 15s. A wide convex portion 15t is provided.
  • the same operation and effect as those of the flow path switching valve 2 of the second embodiment can be obtained. Since the convex surface portion 15t provided on the left surface side (the first main valve seat 13 side) of the first slide valve body 15A is provided away from the end of the annular seal surface 15s in the direction of the axis O, there is no pressure distribution.
  • the pressure (surface pressure) distribution on the annular sealing surface 15s of the first slide valve element (high pressure side slide valve element) 15A can be easily controlled, and the sealability, operability, durability, stability, and the like can be effectively improved.
  • the groove formed between the annular seal surface 15s and the convex surface portion 15t functions as a foreign matter discharge passage, it is also possible to effectively prevent foreign matter accumulation between the annular seal surface 15s and the valve seat surface. it can.
  • the convex portion 15t provided on the left side (the first main valve seat 13 side) of the first slide valve body 15A is formed in the entire width direction of (the outer shape of) the annular seal surface 15s.
  • the convex portion 15t ensures that the annular seal surface 15s of the first slide valve body (high-pressure side slide valve body) 15A opens the port opened in the valve seat surface of the first main valve seat 13 more reliably. It is easy to get over, and it is possible to more effectively prevent the annular seal surface 15 s of the first slide valve body (high-pressure side slide valve body) 15 ⁇ / b> A from being caught by the port, and to prevent the first main valve seat 13 from being caught on the valve seat surface.
  • the rattling of the slide valve body (high pressure side slide valve body) 15A can be further reduced.
  • (Fourth embodiment) 12 and 13 show a fourth embodiment of the flow path switching valve (six-way switching valve) according to the present invention.
  • the flow path switching valve 4 of the fourth embodiment is substantially the same as the flow path switching valve 3 of the third embodiment except for the main valve body. Therefore, the portions corresponding to the respective portions of the flow path switching valve 3 of the third embodiment and the portions having the same functions are denoted by the same reference numerals, and redundant description is omitted. In the following, differences around the main valve body will be described. The explanation will focus on the points.
  • the same operation and effect as those of the flow path switching valve 3 of the third embodiment can be obtained. Since the convex surface portion 15t provided on the left side (the first main valve seat 13 side) of the first slide valve body 15A is provided at least on both sides in the width direction of the annular sealing surface 15s, for example, the first slide valve body is provided. (High-pressure side slide valve element) Even when the valve slides on the valve seat surface of the first main valve seat 13 in a state where 15A is inclined, the annular sealing surface 15s (first slide valve element) 15A of the first slide valve element (high-pressure side slide valve element). Before one side portion of the first main valve seat 13 comes into contact with the valve seat surface of the first main valve seat 13, the convex portion 15t comes into contact with the valve seat surface of the first main valve seat 13, so that the durability is reliably improved. be able to.
  • the contact area between the convex surface portion 15t of the first slide valve body 15A and the valve seat surface of the first main valve seat 13 is smaller than that in the third embodiment, and The pressing force (surface pressure) of the first slide valve body 15A against the valve seat surface of the one main valve seat 13 is increased, and the sealing performance can be further improved.
  • FIGS. 14 and 15 show a fifth embodiment of the flow path switching valve (six-way switching valve) according to the present invention.
  • the flow path switching valve 5 of the fifth embodiment is substantially the same as the flow path switching valve 4 of the fourth embodiment, for example, except for the main valve body. Therefore, the portions corresponding to the respective portions of the flow path switching valve 4 of the fourth embodiment and the portions having the same functions are denoted by the same reference numerals, and redundant description is omitted. In the following, differences around the main valve body will be described. The explanation will focus on the points.
  • the upper end portion and the lower end portion of the annular seal surface 15s provided on the left side (the first main valve seat 13 side) of the first slide valve body 15A have central portions in the width direction.
  • a substantially bar-shaped (two in total) convex portions having the same height as the annular sealing surface 15s and a width smaller than (the outer shape of) the annular sealing surface 15s. 15t are continuously provided, and both sides in the width direction above and below the annular seal surface 15s are spaced apart from (ie, a predetermined gap from) the annular seal surface 15s (the end in the axis O direction).
  • a bar-shaped convex surface 15t is provided.
  • the convex portion 15t in) the flow path switching valve 5 of the present embodiment is different from the flow path switching valve 1 (the convex portion 15t in the flow path switching valve 2) of the first embodiment or the second embodiment. It has a configuration that is combined with (the convex portion 15t in) the flow path switching valve 4 of the fourth embodiment.
  • the configuration in which the main valve body 15 is driven in the main valve chamber 12 using the four-way pilot valve 90 has been described.
  • the main valve body 15 may be driven in the main valve chamber 12 using the above.
  • the six-way switching valve in the heat pump type cooling / heating system has been described as an example, but the number and position of the ports provided in (the main valve chamber 12 of) the main valve housing 11 are described.
  • the configuration and shape of the main valve housing 11 and the configuration and shape of the main valve body 15 and the connecting body 25 disposed in (the main valve chamber 12 of) the main valve housing 11 are not limited to the illustrated example. Needless to say, it is needless to say that the present invention can be applied to a multi-way switching valve other than the six-way switching valve.
  • the flow path switching valves 1 to 5 of the present embodiment can of course be incorporated not only in a heat pump type cooling / heating system, but also in other systems, devices and equipment.

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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)
  • Fluid-Driven Valves (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
PCT/JP2019/030394 2018-08-23 2019-08-02 流路切換弁 Ceased WO2020039889A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP19851650.2A EP3842676B1 (en) 2018-08-23 2019-08-02 Flow channel switching valve
CN201980055106.2A CN112585384B (zh) 2018-08-23 2019-08-02 流路切换阀

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-156507 2018-08-23
JP2018156507A JP6983410B2 (ja) 2018-08-23 2018-08-23 流路切換弁

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WO2020039889A1 true WO2020039889A1 (ja) 2020-02-27

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EP4191105A1 (en) * 2021-12-03 2023-06-07 Airbus Operations, S.L.U. Valve for dividing a hydraulic circuit and hydraulic circuit comprising said valve
US12241485B2 (en) 2021-12-03 2025-03-04 Airbus Operations S.L.U. Valve for dividing a hydraulic circuit and hydraulic circuit comprising said valve

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JP2020029921A (ja) 2020-02-27
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