JP2019049364A - Flow channel switch valve - Google Patents

Abstract

To provide a flow channel switch valve capable of minimizing pressure loss and abrasion of a sliding part, improving sealability, preventing valve leakage, improving durability by securing sufficient strength to endure high pressure, improving pipe arrangement, reducing an occupied space, and the like.SOLUTION: A flow channel switch valve includes: a main valve 5 having a cylindrical main valve housing 10 of which upper and lower openings are air-tightly sealed with a plate-shaped upper valve seat 10A and a lower valve seat 10B, at least three ports 11, 12, 13, 14 in total formed on the upper valve seat 10A and/or the lower valve seat 10B, and a columnar main valve body 20 rotatably disposed in the main valve housing 10; and an actuator 7 for rotating the main valve body 20. A plurality of communication passages 31-34 for selective communication between the ports are disposed in the main valve body 20, and the ports in communication are switched by rotating the main valve body 20.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a rotary type flow path switching valve that switches a flow path by rotating a valve body, and more particularly to a flow path switching valve suitable for performing flow path switching in a heat pump type cooling and heating system.

  In general, heat pump type air conditioning systems such as room air conditioners and car air conditioners, in addition to compressors, outdoor heat exchangers, indoor heat exchangers, expansion valves, etc., flow path switching valves as flow path (flow direction) switching means Is equipped.

  An example of a heat pump type air conditioning system provided with the flow path switching valve will be briefly described with reference to FIG. The heat pump type cooling and heating system 100 in the illustrated example performs switching of the operation mode (cooling operation and heating operation) by the flow path switching valve (four-way switching valve) 140, and basically, the compressor 110 and the outdoor A heat exchanger 120, an indoor heat exchanger 130, and an expansion valve 160, four ports between the compressor 110, the outdoor heat exchanger 120, the indoor heat exchanger 130, and the expansion valve 160, That is, the flow path switching valve 140 having the discharge side high pressure port D, the outdoor side inlet / outlet port C, the indoor side inlet / outlet port E, and the suction side low pressure port S is disposed.

  The respective devices are connected by a flow path formed by a conduit (pipe) or the like, and when the cooling operation mode is selected, the discharge side of the flow path switching valve 140 as shown by a solid arrow in FIG. The high pressure port D is in communication with the outdoor side inlet / outlet port C, and the indoor side inlet / outlet port E is in communication with the suction side low pressure port S. As a result, the refrigerant is drawn into the compressor 110, and the high temperature and high pressure refrigerant is led from the compressor 110 to the outdoor heat exchanger 120 via the flow path switching valve 140, where it exchanges heat with outdoor air and condenses. , And is introduced into the expansion valve 160 as a high-pressure two-phase refrigerant. The high pressure refrigerant is decompressed by the expansion valve 160 and the decompressed low pressure refrigerant is introduced into the indoor heat exchanger 130, where it exchanges heat with the indoor air (cooling) and evaporates, and the low temperature refrigerant from the indoor heat exchanger 130 The low pressure refrigerant is returned to the suction side of the compressor 110 via the flow path switching valve 140.

  On the other hand, when the heating operation mode is selected, the discharge side high pressure port D of the flow path switching valve 140 is set to the indoor side inlet / outlet port E, and the outdoor side inlet / outlet port C is The refrigerant is communicated with the suction side low pressure port S, and the high temperature and high pressure refrigerant is led from the compressor 110 to the indoor heat exchanger 130, where it exchanges heat with the indoor air (heating) and condenses to become a high pressure two-phase refrigerant Is introduced into the expansion valve 160. The high pressure refrigerant is decompressed by the expansion valve 160 and the decompressed low pressure refrigerant is introduced into the outdoor heat exchanger 120, where it exchanges heat with the outdoor air and evaporates, and from the outdoor heat exchanger 120 the low temperature low pressure The refrigerant is returned to the suction side of the compressor 110 via the flow path switching valve 140.

  Conventionally, as a four-way switching valve incorporated in a heat pump type cooling and heating system as described above, there is known one provided with a valve main body (valve housing) incorporating a slide type main valve body and an electromagnetic pilot valve ( See, for example, Patent Document 1). In the flow path switching valve described in Patent Document 1, the discharge side high pressure port D, the outdoor side inlet / outlet port C, the suction side low pressure port S, and the indoor side inlet / outlet port E are formed in the valve housing. A slideable main valve body is disposed slidably in the left-right direction to create a communication state of ports D → C and E → S or ports D → E and C → S (perform flow path switching). . A pair of left and right pairs coupled to the sliding main valve body, to which the high pressure refrigerant on the compressor discharge side and the low pressure refrigerant on the compressor suction side are introduced through the pilot valve on the left and right of the sliding main valve body in the valve housing A high pressure chamber and a low pressure chamber defined by the piston type packing, and the flow path switching is performed by sliding the slide type main valve body in the left and right direction using a pressure difference between the high pressure chamber and the low pressure chamber. Is supposed to do.

  On the other hand, Patent Document 2 proposes a rotary four-way switching valve provided with a pilot valve. The four-way switching valve divides the inside of the cylindrical body (main valve housing) into two by a dividing piece (a plate-like main valve body supported in a cantilever manner on the rotating shaft portion), and on the outer peripheral portion of the main valve housing The discharge-side high-pressure port D and the suction-side low-pressure port S are disposed opposite to each other, and the outdoor inlet-outlet port C and the indoor-side inlet / outlet port E are separated 180 ° back and forth to rotate the plate main valve Thus, the flow path switching, that is, the first communication state in which the discharge side high pressure port D communicates with the outdoor side inlet / outlet port C and the indoor side inlet / outlet port E communicates with the suction side low pressure port S, and the discharge side high pressure port D Creates a second communication state in which the indoor side inlet / outlet port E and the outdoor side inlet / outlet port C communicate with the suction side low pressure port S, and the rotation (flow path switching) of the main valve body is Set on the upper side of the main valve housing Hydraulic actuators using differential pressure between high-pressure refrigerant and low-pressure refrigerant in the system (two divided by a plate-like body cantilevered on an extension shaft portion of a rotation shaft portion of a plate-like main valve body) It is made by selectively performing high pressure refrigerant introduction and discharge to the working chamber with a pilot valve.

JP, 2009-41636, A JP, 2001-82834, A

  In the conventional flow path switching valve as described above, there are problems to be solved as follows.

  That is, in the slide type flow path switching valve described in Patent Document 1, the high-pressure fluid (refrigerant) collides with the inner wall surface etc. in the valve housing with a relatively small inner volume, and the flow direction changes greatly. The pressure loss tends to be large, and the flow path switching is performed by sliding the slide type main valve body with a pair of left and right piston type packings, so the sliding portion is easily worn by stick slip or the like. Along with that, there is also a problem that the sealability of the sliding part is deteriorated and the valve is easily leaked.

  Further, in the rotary type flow path switching valve described in Patent Document 2, since the main valve body receiving high pressure is supported in a cantilever manner, it is a plate-like body having a large pressure receiving area with respect to the plate thickness. As the surface is to be sealed has a cylindrical surface, which has problems such as deformation (deflection) etc., and the surface to be sealed contains a cylindrical surface, the sealability is easily impaired combined with the tendency of the above deformation (deflection) and the like to occur. There is also a problem that it is easy to miss the valve.

  In addition, as the high pressure fluid collides with the plate-like valve body and the inner wall surface in the valve housing and the flow direction is largely changed, the pressure loss becomes large, and the outer circumference four places of the main valve housing are separated by about 90 °. Since the port is provided, the piping management is troublesome, and there is also a problem that the substantial occupied space including the pilot valve and the piping becomes extremely large.

  In addition to the above, in the conventional flow path switching valve, in particular, in the four-way switching valve used in the above-described heat pump type cooling and heating system, a state where the high temperature and high pressure refrigerant and the low temperature and low pressure refrigerant are close in the main valve housing (thin wall Since the flow is performed in a state where one sheet is separated, there is a problem that the amount of heat exchange in those main valve housings becomes large and the efficiency of the system becomes worse.

  Furthermore, in the flow path switching valve described in Patent Document 2 described above, in the fluid pressure type actuator for rotating the main valve body (flow path switching), as in the case of the main valve body, a portion receiving high pressure Since it is a plate-like body with a large pressure receiving area with respect to the plate thickness supported in a cantilevered manner on the extension shaft of the rotary shaft of the plate-like main valve body, deformation (deflection) etc. is easily generated, and strength and durability There's a problem.

  The present invention has been made in view of the above circumstances, and it is possible to suppress pressure loss and wear of sliding parts as much as possible, improve sealing performance, and prevent valve leakage. It is possible to provide a flow path switching valve that can be made difficult, can secure sufficient strength to withstand high pressure, can improve durability, and can also achieve convenience of managing piping, reducing the occupied space, etc. It is in.

  Another object of the present invention is to reduce the amount of internal heat exchange as much as possible when used in an environment where high temperature and high pressure fluid and low temperature and low pressure fluid flow such as a heat pump type air conditioning system. An object of the present invention is to provide a channel switching valve which is designed to be obtained.

  In order to achieve the above object, the flow path switching valve according to the present invention basically comprises at least three cylindrical main valve housings whose openings are hermetically sealed by valve sheets, and at least three of the valve sheets. A main valve having a port provided and a main valve body rotatably disposed in the main valve housing, biasing means for biasing the main valve body toward the valve seat, and the main valve The main valve body is provided with a plurality of communication paths for selectively communicating between the ports, and the main valve body communicates by rotating the main valve body. A ball type seal which is adapted to be switched between ports and which separates the sealing surface on the main valve body side from the valve seat when the main valve body is rotated, between the main valve body and the valve seat. Characterized in that a surface separation mechanism is provided There.

  In a preferred embodiment, at least one first communication passage which allows at least one of the ports to communicate with the other, and one of the ports and another in the main valve body. Between at least one second communication passage which can communicate with each other, and by rotating the main valve body in one direction from between ports communicated by the first communication passage and between ports communicated by the second communication passage The flow path is switched to another, and by rotating the main valve body in the other direction after the flow path is switched, between ports communicated by the second communication path to ports communicated by the first communication path Switching of the flow path is performed.

  In another preferred embodiment, at least one of the plurality of communication passages is formed of a U-shaped passage.

  At the end of the communication passage, preferably, a protrusion having an annular sealing surface closely contacting the opening of each port of the valve seat is provided.

  In another preferred embodiment, the ball type sealing surface separation mechanism accommodates the ball and the ball in a state in which the ball is rotatable and the movement is substantially blocked in a state in which the ball protrudes in the vertical direction. A part of the ball which protrudes from the accommodation part so that the sealing surface by the side of the accommodation part and the main valve body may not separate from the valve seat before the rotation start of the main valve body and at the time of completion of rotation. And a recessed hole having a size and shape such that the ball rolls up while pushing up or pushing down the main valve body when the main valve body rotates, and the ball and the housing portion The recess is provided at two or more locations on the same circumference of the valve body, and the concave hole is on the same circumference of the valve seat, at the same position as the housing portion in plan view and the main valve The angle of rotation Provided position.

  In another preferred aspect, the actuator has a main body portion provided with an operating chamber into which the high pressure fluid supplied to the main valve is introduced, and the pressure of the high pressure fluid is used in the operating chamber. A motion conversion mechanism is provided to convert reciprocating linear motion into rotational motion in both forward and reverse directions.

  In a further preferred aspect, the motion conversion mechanism is configured to receive the pressure receiving moving body accommodated in the working chamber so as to be capable of moving up and down in a state in which the rotation is blocked, and relative movement corresponding to the vertical movement of the pressure receiving moving body. And a rotary drive that is inserted or extrapolated into the pressure receiving movable body, and the outer circumference of the pressure receiving movable body is hermetically sealed between the pressure receiving movable body and the inner circumferential surface of the working chamber to perform the operation A packing for partitioning the chamber into variable volume upper and lower portions is mounted, and the main body portion is provided with an upper port for introducing and discharging high pressure fluid in the upper portion of the working chamber, and high pressure fluid in the lower portion of the working chamber A lower port is provided for introduction and discharge.

  In a further preferred aspect, the actuator introduces the high-pressure fluid into the lower part of the working chamber via the lower port, and discharges the high-pressure fluid from the upper part of the working chamber via the upper port. An upper moving stroke for rotating the rotary driving body in one direction by introducing the high pressure fluid into the upper portion of the working chamber through the upper port, and a high pressure through the lower port from the lower portion of the working chamber By discharging the fluid, it is possible to selectively take a downward movement stroke in which the pressure receiving moving body is moved downward to rotate the rotational driving body in the other direction.

  In a further preferred aspect, switching between the upper and lower moving strokes is performed by a four-way pilot valve connected to the upper port and the lower port, and the high pressure portion and the low pressure portion of the main valve. Be done.

  In a further preferred aspect, the main body of the actuator and the four-way pilot valve are provided on the upper surface side of the upper valve seat or on the lower surface side of the lower valve seat.

  In a preferred embodiment of the flow path switching valve according to the present invention, for example, two out of four communication paths communicating between the ports have a diameter (path diameter) from the start end to the end and the diameter of each port Since the refrigerant flow is straight from the port directly below or directly above, almost no pressure loss occurs in the main valve (main valve body). Further, since the remaining communication passage can also have a relatively large internal volume, pressure loss can be reduced, and in total, pressure loss can be considerably reduced as compared with the conventional flow path switching valve.

  In addition, since the convex part is provided on the main valve body (upper half and lower half) side and the end face is made an annular seal face, the area of the part in contact with the valve seat face needs to be minimum Contact pressure is increased. Thereby, sufficient sealing performance can be secured, and valve leakage can be effectively suppressed.

  In addition, since the upper valve seat and the lower valve seat are flat-shaped, the valve seat surface can be made flat and smooth (the surface accuracy can be easily increased), which also makes it possible to achieve the same as in the conventional example. The sealing performance can be significantly improved as compared with the case where the surface to be sealed includes a cylindrical surface.

  Furthermore, since all ports are provided in the upper valve seat and the lower valve seat of the main valve housing, the piping can be easily managed, and the substantial occupied space including the piping can be reduced.

  Furthermore, by providing the ball type seal surface separation mechanism, the upper half portion of the main valve body is pushed down and the lower half portion is pushed up during rotation of the main valve body (during passage switching). Since the seal surface on the main valve body side is separated from the valve seat surfaces of the upper valve seat and the lower valve seat, sliding friction hardly occurs, so that stick-slip and the like can hardly occur, and the sliding portion The wear of the valve can be significantly suppressed, and furthermore, the wear can be suppressed, so the sealing performance can be improved and the valve leakage can be effectively suppressed.

  Furthermore, in the flow path switching valve according to the present invention, the main valve body (upper half and lower half) receiving high pressure can be made cylindrical, and the communication passage can be provided therein, so the modification as in the conventional example It is hard to occur (deflection) etc., and sufficient strength and durability can be secured.

  In addition to the above, when the flow path switching valve according to the present invention is used in an environment where a high temperature / high pressure refrigerant and a low temperature / low pressure refrigerant flow, such as a heat pump type cooling / heating system, Heat exchange in the main valve housing as compared with the conventional one in which the high-temperature high-pressure refrigerant and the low-temperature low-pressure refrigerant flow in close proximity (a thin wall is separated). The amount can be significantly reduced, which also has the effect of improving the efficiency of the system.

  The subject, composition, and an effect other than the above-mentioned are clarified by the following embodiments.

(A) is a side view of the first embodiment of the flow channel switching valve according to the present invention, (B) is a top layout view of the flow channel switching valve shown in (A), (C) is The lower surface side layout drawing of the flow-path switching valve shown to A). The other side view fractured partially according to the AA arrow line of Drawing 1 (B). The other side view partially broken according to the BB arrow line of FIG. 1 (B). The expanded sectional view of the main valve part which follows the CC arrow line of FIG. 1 (B). FIG. 7 is an enlarged cross-sectional view provided for describing the configuration and operation of a seal surface separation mechanism provided in the flow passage switching valve of the first embodiment. (A) shows a state in which the main valve body is in the first rotation position in the flow path switching valve of the first embodiment, (1) is a plan view on the upper surface side, (2) is XX of (1) (B) shows a state in which the main valve body is in the second rotational position in the flow path switching valve of the first embodiment, (1) is a plan view on the upper surface side, (2) is Sectional drawing according to XX arrow of 1). (A) shows the state in which the first layer member of the main valve body in the first embodiment is in the first rotational position, (1) is a plan view, (2) is a line of arrows XX in (1) 2B shows a state in which the first layer member of the main valve body in the first embodiment is in the second rotational position according to the first embodiment, (1) is a plan view, and (2) is an X of (1) Sectional drawing according to-X arrow line of sight. (A) shows the state in which the second layer member of the main valve body in the first embodiment is in the first rotational position, (1) is a plan view, (2) is a line of arrows XX in (1) 2B shows a state in which the second layer member of the main valve body in the first embodiment is in the second rotational position, (1) is a plan view, and (2) is an X in (1). Sectional drawing according to-X arrow line of sight. (A) shows a state in which the third layer member of the main valve body in the first embodiment is in the first rotational position, (1) is a plan view, (2) is a line of arrows XX in (1) 6B shows a state in which the third layer member of the main valve body in the first embodiment is in the second rotational position according to the first embodiment, (1) is a plan view, and (2) is an X of (1) Sectional drawing according to-X arrow line of sight. (A) shows the state in which the fourth layer member of the main valve body in the first embodiment is in the first rotational position, (1) is a plan view, (2) is a line of arrows XX in (1) (B) shows a state in which the fourth layer member of the main valve body of the first embodiment is in the second rotational position, (1) is a plan view, (2) is an X of (1). Sectional drawing according to-X arrow line of sight. The example which made the upper half part and lower half part of the main valve body of 1st Example the integral thing is shown, (A) is a state in a 1st rotation position, (B) is in a 2nd rotation position. Sectional drawing which each shows a state. The example which made the upper half part and lower half part of the main valve body of 1st Example integral is shown, (A) is a state in a 1st rotation position, (B) is a state in a 2nd rotation position. FIG. The flow-path switching valve of 2nd Example is shown, (A) is a state in which the main valve body is in a 1st rotation position, (B) is rotating 90 degrees clockwise from the 1st rotation position. (1) is a top plan view, (2) is a schematic view showing a communication path configuration in each state, and (3) is a bottom plan view. (A) shows (1) the first layer member, (2) the second layer member, (3) the third layer member, (4) in which the main valve body in the second embodiment is in the first rotational position. The respective plan views of the fourth layer member, (B) shows the communication passage configuration in the state where the main valve body is in the first rotational position, and (1) to (4) of (B) show (A) Sectional drawing according to XX arrow line of (1)-(4) of 2.). (A) shows (1) the first layer member, (2) the second layer member, (3) the third layer member, (4) in the state where the main valve body in the second embodiment is in the second rotational position. The respective plan views of the fourth layer member, (B) shows the communication path configuration in the state where the main valve body is in the second rotational position, and the upper and lower sides of (1) in (B) are Partial sectional views according to the line of arrows U-U and the line of arrows V-V in (1) of (A) respectively, (2) and (3) of (B) are (2) and (3) of (A) Sectional drawing according to a Y-Y arrow line of sight, upper part side and lower side of (4) of (B) are partial sectional views according to a J-J arrow line of (4) of (A) and a K-K arrow line, respectively. The flow-path switching valve of 3rd Example is shown, (A) is a state in which the main valve body is in a 1st rotation position, (B) is a state in which the main valve body is in a 2nd rotation position. ) Is a top plan view, and (2) is a cross-sectional view taken along the line of arrows XX in (1). The partial notch enlarged view of the lower part of FIG. 2 which shows the actuator part in 1st Example of the flow-path switching valve concerning this invention. (A) is a partial expanded sectional view which shows the principal part of the actuator shown by FIG. 17, (B) is a disassembled perspective view of the principal part of the movement conversion mechanism shown by (A). FIG. 18 is a schematic configuration view showing an example of a rotation transmission mechanism used for the actuator shown in FIG. 17; FIG. 18 is a schematic view showing another example of the rotation transmission mechanism used for the actuator shown in FIG. 17; FIG. 18 is a view provided to explain the operation of the actuator shown in FIG. 17; The 17-way pilot valve with which the actuator shown by FIG. 17 is equipped is shown, (A) is an expanded sectional view each showing the time of electricity supply OFF, and (B) each showing an electricity supply ON time. The partial notch enlarged view which shows the other Example of the flow-path switching valve based on this invention. BRIEF DESCRIPTION OF THE DRAWINGS The schematic block diagram which shows an example of a heat pump type air conditioning system.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 shows a first embodiment of a flow channel switching valve according to the present invention, wherein (A) is a side view, (B) is a top side layout view, and (C) is a bottom side layout view. 2, 3 and 4 are other side views partially broken according to the line of arrows A-A in FIG. 1 (B), other side views partially broken according to the lines of arrows B-B, C It is an expanded sectional view of the main valve part in accordance with -C arrow line of sight.

  In the present specification, descriptions representing positions, directions such as upper and lower, right and left, front and rear, etc. are provided for convenience according to the drawings to avoid complicated explanation, and are actually incorporated into a heat pump type air conditioning system etc. It does not necessarily indicate the position or direction in the closed state.

  Further, in each drawing, the gap formed between the members, the separation distance between the members, and the like are large in comparison with the dimensions of the respective constituent members in order to facilitate understanding of the invention and for convenience in drawing. Or it may be drawn small.

[First embodiment of main valve]
The flow path switching valve 1 in the illustrated embodiment is a four-way switching valve, and is used, for example, as the four-way switching valve 140 in the heat pump type cooling and heating system 100 shown in FIG. And a pneumatic actuator 7.

  In the following, first, the main valve 5 will be mainly described, and then the actuator 7 will be described.

  The main valve 5 includes a main valve housing 10 and a main valve body 20 disposed rotatably and vertically movable in the main valve housing 10.

  The main valve housing 10 is made of metal such as aluminum or stainless steel, and is crimped so as to hermetically seal the cylindrical body portion 10C and the upper surface opening of the body portion 10C, and further soldering or brazing A thick disk-shaped upper valve sheet 10A fixed by welding or the like, and a thick disk fixed to the trunk 10C in the same manner as the upper valve sheet 10A so as to close the lower surface opening of the trunk 10C. And a first port 11 and a second port 12 consisting of a pipe joint are provided vertically on the left and right of the upper valve seat 10A, and pipes are provided on the left and right of the lower valve seat 10B. The 3rd port 13 and the 4th port 14 which consist of joints are vertically provided. The ports 11 to 14 are provided on the same circumference, and the first port 11 and the third port 13 and the second port 12 and the fourth port 14 are disposed at the same position in plan view. The lower surface of the upper valve seat 10A and the upper surface of the lower valve seat 10B are flat and smooth valve seat surfaces 17, 17.

  In this embodiment, for example, the first port 11 is a discharge high-pressure port D connected to the compressor discharge side when incorporated in the heat pump type cooling and heating system 100 as shown in FIG. 12 is an indoor side inlet / outlet port E connected to the indoor heat exchanger, the third port 13 is an outdoor side inlet / outlet port C connected to the outdoor heat exchanger, and the fourth port 14 is connected to the compressor suction side And the suction side low pressure port S (see FIG. 1).

  A bearing hole 15A for rotatably supporting an upper rotary shaft portion 30A (described later) of the main valve body 20 at the center on the lower surface side of the upper valve seat 10A in the main valve housing 10 (on the center line O of the main valve housing 10). A recess 19 (a storage portion of a rotation transmission mechanism 70 described later) is provided downward in the vicinity of the center on the lower surface side of the lower valve seat 10B. The bearing hole 15B which supports the lower side rotational shaft part 30B (after-mentioned) of the valve body 20 rotatably is provided.

  Moreover, the main-body part 50 and the pilot valve 80 of the actuator 7 are provided in the back and front of the lower surface side of the lower side valve seat 10B. The main body 50 and the pilot valve 80 do not protrude laterally from the main valve housing 10 in plan view (within the diameter of the lower valve seat 10B).

  The main valve body 20 has a half cylindrical upper half 20A and a lower half 20B. Specifically, the upper half 20A is constituted by the relatively thick first layer member 21 and the second layer member 22 integrally joined to the lower surface side of the first layer member 21 by welding or the like. A lower half 20B is configured by a disc-shaped third layer member 23 and a relatively thick fourth layer member 24 integrally joined to the lower surface side of the third layer member 23 by welding or the like. .

  Between the upper half portion 20A (the second layer member 22) and the lower half portion 20B (the third layer member 23), four compressions as biasing means for biasing them in mutually opposite directions The coil spring 29 is contracted (see FIG. 2). A part of four compression coil springs 29 is provided upward in four spring housing holes 23h (see FIG. 9) provided at equal angular intervals on the same circumference on the upper surface side of the third layer member 23. It is loaded in the protruding state.

  At the same position in plan view on the upper surface side of the first layer member 21 of the main valve body 20 and the lower surface side of the fourth layer member 24, a rectangular cross section passing through the center line O of the main valve body 20 (common to the main valve housing 10) In the vicinity of both ends of the transverse grooves 27, 27, the upper half portion 20A and the lower half portion 20B of the main valve body 20 are integrally rotatable and vertically movable. As shown in FIG. 3, two through holes 26 are formed, and a stepped integral rotating rod 25 having a small diameter portion 25a at the upper and lower ends is inserted into the two through holes 26. It is done.

  The rotary shaft portion of the main valve body 20 is, as shown in FIGS. 2 to 4, an upper rotary shaft portion 30A which can behave integrally with the main portion (upper half portion 20A, lower half portion 20B) of the main valve body 20. And the lower rotation shaft portion 30B. The upper rotary shaft portion 30A is composed of a pivot portion 30a inserted into the bearing hole 15A and a square bar portion 30b of rectangular cross section fitted in the transverse groove 27. The lower rotary shaft portion 30B is composed of a pivot portion 30c inserted into the bearing hole 15B, a rectangular rod portion 30d having a rectangular cross section fitted in the transverse groove 27, and an intermediate large diameter portion 30e. Insertion holes are provided near both ends of the square rod portions 30b and 30d, and the small diameter portions 25a provided at the upper and lower end portions of the integral rotation rod 25 are inserted into the insertion holes, whereby the integral rotation is performed. The rod 25 is fixed to the upper rotation shaft portion 30A and the lower rotation shaft portion 30B.

  Therefore, the upper and lower rotary shaft portions 30A, 30B and the left and right integral pivot rods 25, 25 constitute a frame-like body 28 assembled in a well shape or a rectangular shape so as to be able to move relative to each other slightly and integrally. The frame-like body 28 can flexibly cope with vertical movement, inclination, positional deviation and the like of the main valve body 20 (upper half portion 20A, lower half portion 20B) configured in two.

  When switching the flow path, the main valve body 20 is rotated in both forward and reverse directions by an actuator 7 described later, and from the first rotational position as shown in FIG. A second rotational position as shown in FIG. 6 (B), which is rotated 60 ° clockwise, can be selectively taken.

  In the main valve body 20, when the first rotational position is taken, the first communication passage 31 for communicating the first port 11 with the third port 13 and the second port 12 with the fourth port 14 are communicated. A communication passage 32 is provided, and the third communication passage 33 for connecting the first port 11 and the second port 12 and the communication between the third port 13 and the fourth port 14 when the second rotational position is taken. A fourth communication passage 34 is provided.

  In detail, the upper surface opening or the lower surface opening of each passage portion provided in the first to fourth layer members 21 to 24 which constitute the first to fourth communication passages 31 to 34 are the first to fourth ports. The bores of the first communication passage 31 and the second communication passage 32 are disposed on the same circumference as that of each of the ports 11 to 14 and the bore diameter of each of the ports 11 to 14 is substantially the same. The passage diameter is approximately the same as the diameter of 11-14.

  The first layer member 21 constituting the upper portion of the main valve upper half portion 20A is provided with two straight through passage portions 21A and 21B at an interval of 180 ° as shown in FIG. There are provided two lateral holed passage portions 21C, 21D connected by a horizontal hole 21E in a plan view waveform, the lower surface opening of which is closed by the layer member 22. The lateral holed passage portions 21C and 21D are distributed at an interval of 180 °, and the two together form a U-shaped relatively large volume communication passage (third communication passage 33). The angular distance between the straight through passage portions 21A and 21B and the lateral holed passage portions 21C and 21D is 60 °.

  Therefore, when the main valve body 20 is in the first rotational position, the straight through passage portions 21A and 21B are positioned directly below the first port 11 and the second port 12, and the main valve body 20 is moved from the first rotational position. When rotated clockwise by 60 °, the upper surface openings of the straight through passages 21A and 21B are closed by the upper valve sheet 10A, and the upper surface openings of the horizontal holed passages 21C and 21D are the first port 11 and the second port 12 Located just below the.

  As shown in FIG. 8, two straight through passages 22A and 22B are provided at an interval of 180 ° in the second layer member 22 constituting the lower part of the main valve upper half 20A. The straight through passage portions 22A and 22B are located directly below the straight through passage portions 21A and 21B of the first layer member 21.

  As shown in FIG. 9, two straight through passage portions 23A and 23B are provided at an interval of 180 ° in the third layer member 23 constituting the upper portion of the lower half portion 20B of the main valve body. The straight through passage portions 23A and 23B are located immediately below the straight through passage portions 22A and 22B of the second layer member 22.

  The fourth layer member 24 constituting the lower part of the lower half of the main valve body 20B is, as shown in FIG. 10, similar to the first layer member 21 as shown in FIG. , 24B, and provided with two lateral holed passage portions 24C, 24D connected by a planar-view corrugated lateral hole 24E whose upper surface opening is closed by the third layer member 23. The straight through passage portions 24A, 24B are located directly below the straight through passage portions 23A, 23B of the third layer member 23. The lateral holed passage portions 24C and 24D are disposed at an interval of 180 °, and the two together form a U-shaped relatively large volume communicating passage (fourth communicating passage 34). The angular distance between the straight through passage portions 24A, 24B and the lateral holed passage portions 24C, 24D is 60 °.

  Therefore, when the main valve body 20 is in the first rotational position, the straight through passage portions 24A, 24B are located directly above the third port 13 and the fourth port 14, and the main valve body 20 is in the first rotational position. When rotated clockwise by 60 °, the lower opening of the straight through passage 24A, 24B is closed by the lower valve seat 10B, and the lower opening of the horizontal holed passage 24C, 24D is the third port 13, the fourth Located directly above port 14

  Since the two members of the first layer member 21 and the second layer member 22 are combined to form the communication passage (third communication passage 33), a lateral hole is formed between the lateral holed passage portions 21C and 21D when viewed in cross section. The guide portion bulging to the 21E side is provided relatively long in the direction perpendicular to the center line O. This guiding portion can prevent vortices generated in the portion where the fluid (refrigerant) bends in a U-shape, and the diameter of the horizontal hole 21E and the diameter of each port 11 to 14 have substantially the same passage diameter. Since the volume of the flow path can be made uniform, expansion and contraction of the fluid do not occur in the main valve 5, and the pressure loss can be reduced. If the upper half portion 20A of the main valve body is made of a molded product without using a 3D printer described later, the communication passage has to be a wedge shape without a guide portion, and an eddy current is generated. Because the volume of the flow path can not be made uniform, the pressure loss becomes large.

  The valve seat surfaces 17 of the upper valve seat 10A and the lower valve seat 10B are provided at both ends of each of the communication passages 31, 32, 33, 34, as is well understood with reference to FIGS. , 17 and a convex portion 36 having an annular seal surface 37, 37 closely contacting the opening of each port 11-14. Adjacent convex portions 36 and 36 (the seal surfaces 37 and 37 thereof) are continuously provided to have a shape of glasses in a plan view, and the convex portions 36 provided on the fourth layer member 24 (the seal surface 37) The same is true.

  Further, as shown in FIG. 4, the first communication passage 31 and the second communication passage 32 are divided communication passages that straddle the upper half portion 20A and the lower half portion 20B of the main valve body 20. The following measures have been taken to ensure sealability. That is, to describe the first communication passage 31 as a representative, the large diameter portion 22c is formed in the lower portion of the straight through passage portion 22A of the second layer member 22 constituting the first communication passage 31, and the third layer A cylindrical portion 23c slidably inserted in the large diameter portion 22c is extended at the upper end of the straight through passage portion 23A of the member 23, and an O-ring 49 is provided between the large diameter portion 22c and the cylindrical portion 23c. A washer 49a is attached by welding to the end of the large diameter portion 22c. The second communication passage 32 has a similar configuration.

  In addition to the above, in the present embodiment, the main valve body 20 is disposed between the first layer member 21 and the upper valve sheet 10A of the main valve body 20 and between the fourth layer member 24 and the lower valve sheet 10B. When rotating, the ball type seal surface separation mechanism 45 is provided to separate the seal surfaces 37, 37 on the main valve body 20 side from the valve seat surfaces 17, 17 of the upper valve seat 10A and the lower valve seat 10B.

  The ball-type seal surface separation mechanism 45 is provided between the first layer member 21 and the upper valve seat 10A, as shown in FIGS. 4 and 5 as a representative example. The housing portion 47 which houses the 46 in a state in which a part thereof is vertically protruded and which is freely rotatable and in which the movement is substantially blocked, and before and after the rotation of the main valve body 20 When the main valve body 20 is rotated, a part of the ball 47 projecting from the accommodation portion 47 is fitted so that the seal surface 37 on the main valve body 20 side is not separated from the valve seat surface 17 of the upper valve seat 10A. In (during channel switching), the ball 46 is provided with a reverse conical concave hole 48 sized and rolled out while pushing down the main valve body 20. The housing portion 47 is composed of a round hole 47a and a cylindrical retaining fitting 47b fixed to the round hole 47 by press fitting or the like and having a narrowed upper portion.

  The housing portion 47 in which the ball 46 is housed is the same circle of the first layer member 21 and the fourth layer member 24 of the main valve body 20 as shown in (1) of (A) of FIG. 7 and FIG. They are provided at four locations at intervals of 90 ° on the circumference, and the recessed holes 48 are identical to the housing portion 47 in plan view on the same circumference of the upper valve seat 10A and the lower valve seat 10B. It is provided in a total of eight places, a position away from the said position, and 60 degrees clockwise.

  In the seal surface separation mechanism 45, before the start of rotation of the main valve body 20 and at the time of the end of rotation, as shown in FIG. 5A, a part of the ball 46 is in the recessed hole 48 of the upper valve seat 10A. I'm stuck. The amount of fitting (height from the valve seat surface 17 of the upper valve seat 10A to the top of the ball 46) is h. From this state, when the main valve body 20 starts to be rotated by 60 °, the housing portion 47 moves (rotates) in the circumferential direction, and accordingly, the ball 46 is, as shown in FIG. 5B, the main valve body The roller 20 (upper half 20A) rolls out of the recessed hole 48 while being pushed down against the biasing force of the compression coil spring 29 that is compressed between the upper half 20A and the lower half 20B. Thereby, the seal surface 37 of the main valve body 20 is separated from the valve seat surface 17 of the upper valve seat 10A. The amount of depression of the main valve body 20 at this time is the fitting amount h.

  When the main valve body 20 rotates 60 °, the ball 46 is fitted into the next recessed hole 48, so the main valve body 20 (upper half 20A) is pushed up by the biasing force of the compression coil spring 29, and the main valve body Twenty sealing surfaces 37 are pressed against the valve seat surface 17 of the upper valve seat 10A.

  As understood from the above description, when the main valve body 20 assumes the first rotational position, the first communication passage 31 communicating the first port 11 and the third port 13 is the straight through passage portion 21A, 22A, 23A, and 24A, and the second communication passage 32 for communicating the second port 12 with the fourth port 14 is a straight through passage portion 21B, 22B, 23B, and 24B. It will be a straight passage configured.

  On the other hand, when the main valve body 20 assumes the second rotational position, the third communication passage 33 for communicating the first port 11 with the second port 12 is provided in the upper half 20A of the main valve body 20. A fourth communication passage 34 is formed in the lower half 20B of the main valve body 20. The fourth communication passage 34 is a U-shaped passage configured by the horizontal holed passage portions 21C and 21D and causes the third port 13 and the fourth port 14 to communicate. It becomes a U-shaped passage which is composed of the lateral holed passage portions 24C and 24D.

  As described above, in the flow path switching valve 1 of the present embodiment, the main valve body 20 is rotated 60 ° clockwise from the first rotation position, so that the port 11-13 communicated by the first communication passage 31 is communicated. And switching of the flow path from between the ports 12-14 communicated by the second communication passage 32 between the ports 11-12 communicated by the third communication passage 33 and between the ports 13-14 communicated by the fourth communication passage is performed. Between the ports 11-12 communicated by the third communication passage 33 and the ports 13-14 communicated by the fourth communication passage by rotating the main valve body 20 counterclockwise from the second rotational position by 60 °. Then, switching of the flow path between the ports 11-13 communicated by the first communication passage 31 and the ports 12-14 communicated by the second communication passage 32 is performed.

  When the flow path switching valve 1 of the present embodiment is incorporated into a heat pump type cooling and heating system as shown in FIG. 24, for example, the first port 11 is connected to the compressor discharge side as described above. The high pressure port D, the second port 12 is the indoor side inlet / outlet port E connected to the indoor heat exchanger, the third port 13 is the outdoor side inlet / outlet port C connected to the outdoor heat exchanger, and the fourth port 14 is the compressor suction side The suction side low pressure port S is connected to the

  Then, when performing the cooling operation, the main valve body 20 is made to assume the first rotational position as shown in FIG. Thus, as indicated by the white arrow in (2) of FIG. 6A, the high pressure refrigerant from the compressor is discharged from the high pressure port 11 (D) on the discharge side → the linear first communication passage 31 While flowing to the port 13 (C), the low pressure refrigerant from the indoor heat exchanger flows from the indoor side inlet / outlet port 12 (E) → the linear second communication passage 32 → the suction side low pressure port 14 (S).

  On the other hand, when the heating operation is performed, the main valve body 20 is rotated 60 ° clockwise from the first rotation position to take the second rotation position as shown in FIG. 6 (B). As a result, the flow path is switched, and as shown by the outlined arrow in (2) of FIG. 6B, the high pressure refrigerant from the compressor is discharged on the high pressure port 11 (D) → U shape. While flowing from the third communication passage 33 to the indoor side inlet / outlet port 12 (E), the low pressure refrigerant from the outdoor heat exchanger flows from the outdoor side inlet / outlet port 13 (C) to the reverse U-shaped fourth communication passage 34 to suction It flows to the side low pressure port 14 (S).

  In the flow path switching valve 1 according to the present embodiment configured as described above, the first communication path 31 and the second communication path 32 have a thickness (path diameter) from the start end to the end thereof of the first port 11 and the second port. It is a straight passage substantially the same as the diameter of the port 12, and the refrigerant flows straight from the first port 11 and the second port 12 straight down, so that almost pressure loss in the main valve 5 (main valve body 20) occurs. Absent. Further, since the third communication passage 33 and the fourth communication passage 34 configured by the two horizontal holed passage portions 21C and 21D, 24C and 24D have a relatively large internal volume, the pressure loss is reduced, and the total Thus, the pressure loss can be considerably reduced as compared with the conventional flow path switching valve.

  Further, the main valve body 20 is divided into two parts of an upper half 20A and a lower half 20B, and the upper half 20A and the lower half 20B can be moved up and down independently, and the upper half Since the compression coil spring 29 is compressed between the lower half 20B and the lower half 20B, the upper half 20A is pushed up by the spring force and the sealing surface 37 thereof is at the valve seat surface 17 of the upper valve seat 10A. While being pressed around each port 11, 12, the lower half 20B is pushed down so that its sealing surface 37 is pressed around each port 13, 14 in the valve seat surface 17 of the lower valve seat 10B.

  In this case, since the convex portion 36 is provided on the main valve body 20 (upper half 20A and lower half 20B) side and the end face thereof is the annular seal surface 37, the part that contacts the valve seat surface 17 The surface area of the contact surface is minimized, so the contact pressure is increased. Thereby, sufficient sealing performance can be secured, and valve leakage where fluid (refrigerant) leaks from the sliding surface of the main valve body 20 can be effectively suppressed.

  In addition, since the upper valve seat 10A and the lower valve seat 10B are flat-shaped, the valve seat surface 17 can be made flat and smooth (the surface accuracy can be easily increased). As compared with the case where the surface to be sealed includes a cylindrical surface like this, the sealing performance can be remarkably improved.

  Furthermore, since all the ports 11 to 14 are provided in the upper valve seat 10A and the lower valve seat 10B of the main valve housing 10, piping can be easily managed, and the substantial occupied space including the piping can be reduced. it can.

  Furthermore, in the present embodiment, the upper half 20A of the main valve body 20 is pushed down by the ball type seal surface separation mechanism 45 when the main valve body 20 is rotating (during flow path switching). Since the half portion 20B is pushed up and the seal surfaces 37, 37 on the main valve body 20 side are separated from the valve seat surfaces 17, 17 of the upper valve seat 10A and the lower valve seat 10B, most of the sliding friction is As a result, it is difficult to cause stick-slip and the like, abrasion of the sliding part can be greatly suppressed, and further, since the abrasion is suppressed, the sealing property is improved and the valve leakage is effectively suppressed. be able to.

  Further, in the four-way switching valve having the conventional slide type main valve body as shown in Patent Document 1, the flow passage opening area between the high pressure pipe D and the low pressure pipe S changes rapidly when the flow path is switched, Abnormal noise (switching noise) is generated when the high pressure refrigerant enters the low pressure pipe at a stretch. In order to prevent this abnormal noise, the frequency of the compressor is gradually decreased on the air conditioning and heating system side so that the differential pressure due to the pressure difference between the high pressure pipe D and the low pressure pipe S becomes an acceptable differential pressure. It was necessary to switch the flow path from In the flow path switching valve 1 of the present embodiment, the main valve body is floated from the valve seat surface by the ball type seal surface separation mechanism 45 after the insertion amount h is increased, and then switching is performed. As a result, the opening area of the flow passage between the high pressure pipe D and the low pressure pipe S does not change rapidly, and hence the generation of the above-mentioned abnormal noise can be suppressed. In addition, the degree of reduction of the frequency of the compressor at the time of flow path switching can be made smaller than that of the cooling and heating system using the four-way switching valve of Patent Document 1 by changing the fitting amount h appropriately. It is also possible to switch the flow path without lowering the

  Furthermore, in the flow path switching valve 1 of the present embodiment, the main valve body 20 (upper half 20A and lower half 20B) receiving high pressure is made cylindrical, and the communication paths 31 to 34 are provided inside thereof. The deformation (deflection) as in the conventional example does not easily occur, and sufficient strength and durability can be ensured.

  In addition to the above, when the flow path switching valve 1 of the present embodiment is used in an environment where a high-temperature and high-pressure refrigerant and a low-temperature and low-pressure refrigerant flow, such as a heat pump type cooling and heating system, each communication passage 31 to 34 is a main valve body 20 The main valve is provided relatively widely inside, so compared to the conventional one in which the high-temperature high-pressure refrigerant and the low-temperature low-pressure refrigerant flow close to each other (a thin wall is separated). The amount of heat exchange in the housing can be greatly reduced, and thus the effect of improving the efficiency of the system can be obtained.

  Next, a modification of the main valve body of the first embodiment described above will be described.

  FIG. 11 shows an example in which the upper half 20A and the lower half 20B of the main valve body 20 of the first embodiment are integrated. That is, in the first embodiment, the upper half 20A of the first layer member 21 and the second layer member 22 joined thereto, and the third layer member 23 and the fourth layer member joined thereto. The lower half 20B is configured by 24. However, in this example, the upper half 20A and the lower half 20B are respectively manufactured as an integral body from the beginning with a 3D printer or the like. The other configuration is the same as that of the first embodiment, and substantially the same effect as that of the first embodiment can be obtained.

  FIG. 12 shows an example in which the upper half 20A and the lower half 20B of the main valve body 20 of the first embodiment are integrated. That is, the entire main valve body 20 (first to fourth layer members 21 to 24) is manufactured as an integral body from the beginning by a 3D printer or the like. In this example, it is difficult to provide means for biasing the main valve body 20 in the vertical direction, so it is difficult to ensure the required sealing performance.

[Second embodiment of main valve]
Hereinafter, the flow path switching valve 2 of the second embodiment of the present invention will be described with reference to FIGS.

  The flow passage switching valve 2 of the second embodiment differs from the first embodiment only in the configuration of the communication passage provided in the main valve body 20 of the first embodiment, and the other configuration is substantially the same. The parts common to the flow path switching valve 1 are simplified or omitted from the drawing, and in the following, only the differences (the communication path configuration) will be mainly described. In addition, in FIGS. 13-15, the same code | symbol is attached | subjected to the part corresponding to each part of the flow-path switching valve 1 of 1st Example.

  FIG. 13A shows a state where the main valve body 20 is in the first rotational position, and FIG. 13B shows a second rotation where the main valve body 20 is rotated 90 ° clockwise from the first rotational position. The state which exists in a position is shown, (1) is an upper surface side layout drawing, (2) is the schematic which shows the communicating path structure in each state, (3) is a lower surface side layout drawing.

  (A) of FIG. 14 shows (1) the first layer member 21, (2) the second layer member 22, (3) the third state where the main valve body 20 in the second embodiment is in the first rotational position. The top view of each of the three-layer member 23, (4) the fourth layer member 24, (B) shows the communication passage configuration in a state where the main valve body 20 is in the first rotational position, and (1) of (B) ]-(4) is sectional drawing according to XX arrow line of (1)-(4) of (A).

  FIG. 15 (A) shows (1) the first layer member 21, (2) the second layer member 22, (3) the third layer member 23, ((3)), with the main valve body 20 in the second rotational position. 4) Each top view of the 4th layer member 24, (B) shows the communication passage composition in the state where the main valve body 20 is in the 2nd rotation position, upper row side of (1) of (B), lower row The side is a partial sectional view according to the line of arrows U-U and V-V in (1) of (A) respectively, (2) and (3) of (B) are (2) and (2) of (A) Sectional view according to the YY arrow line of 3), the upper and lower sides of (4) of (B) are partial cross sections according to the J-J arrow line of (A) and (K) arrow respectively FIG.

  When the flow path switching valve 2 of this embodiment is incorporated into a heat pump type air conditioning system as shown in FIG. 24, unlike the first embodiment, for example, the first port 11 is connected to the compressor discharge side. Discharge-side high-pressure port D, the second port 12 is a suction-side low-pressure port S connected to the compressor suction side, the third port 13 is an outdoor outside-in / out port C connected to an outdoor heat exchanger, the fourth port 14 It is set as the indoor side entrance / exit port E connected to an indoor heat exchanger.

  And, when the main valve body 20 of the flow path switching valve 2 of the second embodiment takes the first rotational position, the first communication passage 41 and the third communication passage that make the first port 11 communicate with the third port 13 A second communication passage 42 is provided to communicate the four ports 14 and the second port 12, and when the second rotational position rotated 90 ° clockwise from the first rotational position is taken, the first port 11 A third communication passage 43 communicating with the fourth port 14 and a fourth communication passage 44 communicating the third port 13 with the second port 12 are provided.

  In order to form the first to fourth communication passages 41 to 44, four passage portions are provided in each of the first to fourth layer members 21 to 24 constituting the main valve body 20, and The upper surface openings of the four passage portions provided in the first layer member 21 and the lower surface openings of the four passage portions provided in the fourth layer member 24 have the same circumference as the first to fourth ports 11 to 14. The diameter of the first communication passage 41 and the diameter of the second communication passage 42 are substantially the same as the diameters of the ports 11-14. It is the road diameter.

  The first layer member 21 constituting the upper portion of the main valve upper half portion 20A, like the straight through passage portions 21A and 21B of the first embodiment, has two linear through passage portions 41A, spaced by 180.degree. 41B is provided. In addition, as shown in the upper and lower sides of (1) in FIG. 15B, the horizontal holed passage portions 41C and 41D are open at one end (upper surface openings 41a and 41c) and the entire lower surface is open. Provided. The upper surface openings 41a and 41c of the horizontal holed passage portions 41C and 41D are disposed at positions 90 ° apart from the straight through passage portions 41A and 41B, and the lower surface openings other than the other end are closed by the second layer member 22. The other end (lower surface openings 41b and 41d) not closed by the second layer member 22 is disposed on a straight line connecting the centers of the straight through passage portions 41A and 41B.

  Therefore, when the main valve body 20 is in the first rotational position, the straight through passage portions 41A and 41B are located directly below the first port 11 and the second port 12, and the main valve body 20 is moved from the first rotational position. When rotated clockwise by 90 °, the upper surface openings of the straight through passages 41A and 41B are closed by the upper valve sheet 10A, and the upper surface openings of the lateral holed passages 41D and 41C are the first port 11 and the second port 12 Located just below the.

  In the second layer member 22 constituting the lower portion of the main valve upper half portion 20A, four straight lines are formed at predetermined intervals on the straight line connecting the centers of the straight through passage portions 41A and 41B of the first layer member 21 described above. Through passage portions 42A, 42B, 42C, 42D are provided. The straight through passage portions 42A, 42D are located directly below the straight through passage portions 41A, 41B of the first layer member 21. The straight through passage portion 42B is located immediately below the lower surface opening 41b of the horizontal holed passage portion 41C, and the straight through passage portion 42C is located immediately below the lower surface opening 41d of the horizontal holed passage portion 41D.

  In the third layer member 23 constituting the upper portion of the lower half portion 20B of the main valve body, the four straight through passages 42A, 42B, 42C, 42D provided in the second layer member 22 are directly penetrated four straight Road portions 43A, 43B, 43C, 43D are provided.

  Like the straight through passages 21A and 21B of the first embodiment, the fourth layer member 24 constituting the lower part of the lower half 20B of the main valve body has two straight through passages 44A separated by 180 °, 44B is provided. In addition, as shown in the upper and lower sides of (4) in FIG. 15B, the horizontal holed passage portions 44C and 44D are open at one end (lower surface openings 44a and 44c) and the entire upper surface is open. Provided. The lower surface openings 44a and 44c of the horizontal holed passage portions 44C and 44D are disposed at positions 90 ° apart from the straight through passage portions 41A and 41B, and the upper surface openings other than the other end are closed by the third layer member 23. The other end (upper surface openings 44b and 44d) not closed by the third layer member 23 is disposed on a straight line connecting the centers of the straight through passage portions 44A and 44B.

  Therefore, when the main valve body 20 is in the first rotational position, the straight through passage portions 44A and 44B are positioned directly above the third port 13 and the fourth port 14, and the main valve body 20 is in the first rotational position. When rotated 90 ° clockwise, the lower surface openings of the straight through passage portions 44A and 44B are closed by the lower valve sheet 10B, and the lower surface openings 44c and 44a of the horizontal holed passage portions 44D and 44C are the third port 13 , And directly above the fourth port 14.

  As understood from the above description, when the main valve body 20 assumes the first rotational position, the first communication passage 41 communicating the first port 11 and the third port 13 is a straight through passage portion 41A, The second communication passage 42 for connecting the fourth port 14 and the second port 12 by the straight through passages 41B, 42D, 43D, and 44B is a linear passage formed by 42A, 43A, and 44A. It will be a straight passage configured.

  On the other hand, when the main valve body 20 assumes the second rotational position, the third communication passage 43 which causes the first port 11 and the fourth port 14 to communicate is in order from the top, the passage portion 41D with a horizontal hole → straight through passage portion 42C → straight through passage portion 43C → lateral holed passage portion 44C. In addition, the fourth communication passage 44 for communicating the third port 13 and the second port 12 includes, in order from the bottom, a passage portion 44D with a horizontal hole → a straight through passage 43B → a straight through passage 42B → a passage 41C with a horizontal hole It becomes a crank-like passage.

  As described above, in the flow path switching valve 2 of the present embodiment, the main valve body 20 is rotated 90 ° clockwise from the first rotation position, so that the port 11-13 communicated by the first communication passage 41 is communicated. And switching of the flow path from between the ports 14-12 communicated by the second communication passage 42 between the ports 11-14 communicated by the third communication passage 43 and between the ports 13-12 communicated by the fourth communication passage Between the ports 11-14 communicated by the third communication passage 43 and between the ports 13-12 communicated by the fourth communication passage by rotating the main valve body 20 counterclockwise from the second rotational position by 90 °. Then, the flow paths are switched between the ports 11-13 communicated by the first communication passage 41 and the ports 14-12 communicated by the second communication passage 42.

  In the case where the flow path switching valve 2 of this embodiment is incorporated into a heat pump type cooling and heating system as shown in FIG. 24 to perform a cooling operation, the main valve body 20 is shown in (1) of FIG. The first rotational position is taken. Accordingly, as indicated by the outlined arrow in (2) of FIG. 13A, the high pressure refrigerant from the compressor is discharged from the high pressure port 11 (D) on the discharge side → the linear first communication passage 41 While flowing to the port 13 (C), the low pressure refrigerant from the indoor heat exchanger flows from the indoor side inlet / outlet port 14 (E) → the linear second communication passage 42 → the suction side low pressure port 12 (S).

  On the other hand, when the heating operation is performed, the main valve body 20 is rotated 90 ° clockwise from the first rotation position, and the second rotation position as shown in (1) of FIG. Let As a result, the flow path is switched, and as indicated by the outlined arrow in (2) of FIG. 13B, the high pressure refrigerant from the compressor is discharged from the discharge side high pressure port 11 (D) → the crank 3 communication passage 43 → inside room inlet / outlet port 14 (E), and the low pressure refrigerant from the outdoor heat exchanger is outside chamber inlet / outlet port 13 (C) → crank-like fourth communication passage 44 → intake side low pressure port It flows to 12 (S).

  Also in the flow path switching valve 2 of this embodiment configured as such, substantially the same function and effect as the first embodiment can be obtained.

[Third embodiment of main valve]
FIG. 16 shows the flow passage switching valve of the third embodiment, in which (A) shows the state in which the main valve body is in the first rotational position, and (B) shows the state in which the main valve body is in the second rotational position. (1) is a top plan view, and (2) is a cross-sectional view taken along the line of arrows XX in (1). In FIG. 16, parts corresponding to the parts of the flow path switching valve 1 of the first embodiment are denoted by the same reference numerals.

  The flow path switching valve 3 of the third embodiment is a three-way switching valve, and there is no second port 12 provided in the main valve housing 10 of the first embodiment, and the first layer member 21 and the second layer It is integrated with the member 22 (because it is not necessary to form a U-shaped communication passage (third communication passage 33)), and the second communication passage 32 and the third communication passage 33 in the first embodiment are configured. The straight through passage portions 21B, 22B, 23B, and 24B, the horizontal holed passage portions 21C and 21D, and the portions associated therewith are deleted.

  Therefore, in the flow path switching valve 3 of the third embodiment, the main valve body 20 is rotated 60 ° clockwise from the first rotational position, from between the ports 11-13 communicated by the first communication passage 31. The flow path is switched between the ports 13-14 communicated by the fourth communication passage 34, and the main valve body 20 is rotated 60 ° counterclockwise from the second rotational position, thereby the fourth communication passage 34. The switching of the flow path from between the ports 13-14 in communication with each other and between the ports 11-13 in communication with the first communication path 31 is performed.

  Also in the flow path switching valve 3 of this embodiment configured as above, although there is a difference between the three-way switching valve and the four-way switching valve, substantially the same function and effect as the four-way switching valve 1 of the first embodiment can be obtained. Be

  When the three-way switching valve 3 of this embodiment is used in the above-described heat pump type air conditioning system, two three-way switching valves 3 are used to act as a four-way switching valve, or a refrigerant or cold air / warm air supply destination (For example, switching between sending to one of the two rooms or sending to the other).

[Embodiment of actuator]
Next, the actuator 7 for rotating the main valve body 20 in the flow path switching valve 1 of the first embodiment will be described with reference to FIGS. 17 to 22. FIG.

  The actuator 7 according to the first embodiment is a fluid pressure type that utilizes the differential pressure between the high pressure fluid and the low pressure fluid flowing in the main valve 5 and is disposed on one end side of the lower valve seat 10B in the main valve housing 10. It has a main body 50 provided. The main body 50 is fixed by caulking so as to airtightly seal the lower surface opening of the cylindrical body 51 extended downward from the lower valve seat 10B and the lower surface of the body 51. A thick disk-shaped seal which is fixed by caulking so as to seal the lower surface closing member 52 having a convex portion 52a at the center and the upper surface opening of the body 51 and is further fixed by soldering, brazing, welding or the like The upper surface closing member 53 which also serves as a member and a stopper is provided, and an operation chamber 55 is provided therein, and a thick-walled bottomed cylindrical pressure receiving moving member 60 constituting the motion conversion mechanism 58 is provided in the operation chamber 55. The short pressure roller moving member 60 is accommodated in the pressure receiving moving member 60. The short cylindrical rotation driving member 65 is rotatably inserted relative to the vertical movement of the pressure receiving moving member 60. Since the rotary drive 65 is pivotally supported with respect to the main body 50, it does not move in the working chamber 55 in the vertical direction, but relative to the movement of the pressure receiving moving body 60 in the vertical direction. The pressure receiving member 60 is pivoted within the pressure receiving moving member 60 (to be described in detail later).

  In the vicinity of the outer peripheral lower end of the pressure receiving moving body 60, a packing for airtightly sealing between the inner peripheral surface of the working chamber 55 and airtightly dividing the working chamber 55 into an upper portion 55A and a lower portion 55B of variable volume. 62 is mounted, and at the upper part of the outer periphery of the pressure receiving moving body 60, an operating pin 63 which is fitted in a key groove 54 extending in the height direction provided at the left and right two places on the inner peripheral upper half of the body 51 It is fixed by press fitting etc.

  By means of the operation pin 63 and the key groove 54, the pressure receiving moving body 60 linearly moves up and down, but its rotation is blocked.

  Note that FIG. 17 shows a state where the pressure receiving movable body 60 is at the lowest position (downward stroke completed state), and a state where the pressure receiving movable body 60 is at the highest position (upper Motion complete) is shown (detailed later).

  Further, an upper port 56 for introducing and discharging high pressure fluid to and from the upper portion 55A of the working chamber is provided at the top of the main body 50, and a high pressure fluid is applied to the lower portion 55B of the lower portion (lower surface closing member 52). A lower port 57 is provided for introducing and discharging the

  In the actuator 7 of this embodiment, the vertical movement (reciprocation linear movement) of the pressure receiving moving body 60 is performed between the pressure receiving moving body 60 and the rotary driving body 65 which constitute the motion converting mechanism 58. A ball 72, a housing 74 for the ball 72, and a spiral groove 75 are provided to convert it into rotational movement in both forward and reverse directions 65.

  More specifically, the pressure receiving moving body 60 is provided with a plurality (two in the present embodiment) of balls 72 and the housing portions 74 thereof, and the rotation driving body 65 is bent in the circumferential direction around the upper and lower A plurality of (two in the present embodiment) spiral grooves 75 extending in the direction are provided. In the state where the ball 72 is caused to project radially inward by the ball 72 by the upper end portion of the pressure receiving moving body 60 and the annular pressing member 66 joined to the upper end portion by welding or the like. , And rotatably accommodated in a substantially blocked state, and the spiral groove 75 is rotated by fitting a part of the ball 72 projecting radially inward from the accommodation portion 74 into engagement. It consists of a shallow groove with an arc-shaped cross section that can be in close contact freely.

  A rotary drive shaft 76 is crimped and fixed at the center of the rotary drive 65 so as to rotate integrally with the rotary drive 65. The rotary drive shaft 76 rotates in a lower large diameter portion 76a whose lower portion is fixed to the rotary drive 65, an intermediate portion 76b following it, and a bearing hole 16 provided on the lower surface side of the lower valve seat 10B. It consists of a small diameter pivot portion 76c which is freely supported. The lower large diameter portion 76a of the rotary drive shaft 76 is, from the lower side, an insertion portion 76aa which is passed through the central hole of the rotary drive 65, and the diameter of the insertion portion 76aa is larger than that of the insertion portion 76aa. A first enlarged diameter portion 76 ab passing through the central hole, and a second enlarged diameter portion 76 ac (the upper surface closing member 53 and the drive arm 78 of the rotation transmission mechanism 77 further expanded in diameter than the first enlarged diameter portion 76 ab An O-ring 59 is interposed between the central hole of the upper surface closing member 53 and the first enlarged diameter portion 76ab.

  The rotational drive shaft 76 and the rotational drive fixed to the rotational drive shaft 76 come in contact with each other by bringing the lower step surface of the step formed by the first enlarged diameter portion 76 ab and the second enlarged diameter portion 76 ac into contact with the upper surface of the upper surface closing member 53. The body 65 is prevented from falling off, and the downward step surface of the step formed by the insertion portion 76aa and the first enlarged diameter portion 76ab is used for caulking and fixing the rotary drive body 65 to the rotary drive shaft portion 76. It is considered as the receiving side.

  Here, the rotation axis Q (rotation drive shaft 76) of the rotation drive body 65 is eccentric to the rotation axis O of the main valve body 20 and is disposed parallel to the rotation axis O of the main valve body 20. Between the rotary drive shaft 76 and the lower rotary shaft 30B of the main valve body 20, a rotation transmission mechanism 77 for transmitting the rotation of the rotary drive 65 to the main valve 20 is provided.

  The proximal end portion of the rotation transmission mechanism 77 is connected and fixed to the middle portion 76b of the rotary drive shaft portion 76, as is well understood by referring to FIG. 19 in addition to FIG. 17 and FIG. The proximal end portion of the drive arm 78 having a U-shaped engaging groove 78a formed therein and the pivot shaft portion 30c of the lower rotary shaft portion 30B of the main valve body 20 is connected and fixed, and the U-shaped An engaging pin 79 slidably engaged with the engaging groove 78a is composed of a driven arm 39 hanging downward.

  In the rotation transmission mechanism 77 having such a configuration, when the rotation drive shaft 76 rotates, the drive arm 78 rotates (rocks) integrally therewith, and in accordance with this, the vicinity of the tip of the driven arm 39 (engagement pin 79) is driven The lower rotating shaft portion 30B and the main valve body 20 are rotated by being rotated near the tip of the arm 78 (U-shaped engagement groove 78a). In this case, in the present embodiment, the rotation angle θ of the driven arm 39 is 60 °, which is the rotation angle required for the main valve body 20 to switch the flow path as described above. The rotation angle θ is set by the stroke length of the vertical movement of the pressure receiving moving body 60, the lever ratio of the drive arm 78 and the driven arm 39, and the like. Note that FIGS. 17 and 18A, and FIGS. 21A to 21D described later show the states during the rotation of the drive arm 78 and the driven arm 39.

  Further, as a rotation transmission mechanism, as shown in FIG. 20, a driven gear 97 connected and fixed to the rotary drive shaft 76 and a driven gear connected and fixed to the lower rotary shaft 30B and meshed with the drive gear 97. It may be configured by the gear 98 and the like.

  Next, the operation in the main body 50 of the actuator 7 will be described (the configuration of the four-way pilot valve 80 and the operation using it will be described later).

  FIGS. 17 and 21A show a state in which the high pressure fluid (high pressure refrigerant) is introduced to the working chamber upper portion 55A through the upper port 56 and the high pressure fluid is discharged from the working chamber lower portion 55B through the lower port 57. It shows. When a high pressure fluid is introduced into the working chamber upper portion 55A, the high pressure fluid reaches the corners of the space (the working chamber upper portion 55A) above the packing 62 attached to the pressure receiving moving body 60 and below the top surface closing member 53. A portion between the bottom surface of the pressure receiving moving body 60 and the lower surface of the rotation driving body 65 with a gap formed between the inner peripheral surface of the pressure receiving moving body 60 and the outer peripheral surface of the rotation driving body 65 The pressure receiving area on the upper surface side of the pressure receiving moving body 60 is equal to the pressure receiving area on the lower surface side, since it extends to the gap portion formed between the inner peripheral surface of the trunk 51 and the outer peripheral surface of the pressure receiving moving body 60.

  Under such a configuration, in the state shown in FIGS. 17 and 21A, a high pressure fluid is introduced to the lower working chamber 55B via the lower port 57, and the upper port 56 is opened from the upper working chamber 55A. When the high pressure fluid is discharged, the pressure in the lower portion 55B is higher than that in the upper portion 55A. Therefore, the pressure receiving moving body 60 is pushed upward, and the operating pin 63 of the pressure receiving moving body 60 is guided to the key groove 54 While being moved, the pressure receiving moving body 60 moves upward straightly, and the ball 72 of the movement converting mechanism 58 also moves upward while rotating. At this time, the spiral groove 75 is pushed in the circumferential direction by the portion of the ball 72 fitted into the spiral groove 75, and the rotary drive 65 rotates in one direction (here, clockwise). When the upper end (annular pressing member 66) of the pressure receiving moving body 60 abuts on the upper surface closing member 53, the upward movement of the pressure receiving moving body 60 is stopped, and the rotation of the rotation driving body 65 is also stopped. Hereinafter, this stroke will be referred to as an upper stroke, and the state shown in FIG. 21B (a state in which the pressure receiving movable body 60 is at the highest position) will be referred to as an upper stroke completion state.

  On the other hand, as shown in FIGS. 21C and 21D, in the upper movement stroke completion state, high pressure fluid is introduced to the upper portion 55A of the working chamber via the upper port 56, and the lower portion from the lower portion 55B. When the high pressure fluid is discharged through the port 57, the pressure in the working chamber upper portion 55A is higher than that in the working chamber lower portion 55B. Therefore, the pressure receiving moving body 60 is pushed downward and the operating pin 63 of the pressure receiving moving body 60 is a key groove While being guided by 54, the pressure receiving moving body 60 moves down straight, and the ball 72 of the motion conversion mechanism 58 also moves down straight while rotating. At this time, the spiral groove 75 is pushed in the circumferential direction by the portion of the ball 72 fitted into the spiral groove 75, and the rotary driver 65 rotates in the other direction (counterclockwise here). When the lower end of the pressure receiving moving body 60 abuts on the convex portion 52 a of the lower surface closing member 52, the downward movement of the pressure receiving moving body 60 is stopped, and the rotation of the rotation driving body 65 is also stopped. Hereinafter, this stroke is referred to as a downward movement stroke, and the state shown in FIG. 21D (a state in which the pressure receiving moving body 60 is at the lowest position) is referred to as a downward movement stroke completion state.

  The main valve body 20 is rotated from the first rotational position to the second rotational position by causing the pressure receiving moving body 60 to take the lower movement stroke in the upper movement stroke completion state, and the flow path switching as described above is performed. And the main valve body 20 is rotated from the second rotational position to the first rotational position by causing the pressure receiving moving body 60 to take the upper moving stroke in the lower moving stroke completion state. Channel switching as described above is performed.

  In this embodiment, the flow path switching, that is, the switching between the upper and lower moving strokes, is performed by the upper port 56 and the lower port 57, and the inside of the main valve housing 10 which is a high pressure portion and the low pressure portion An electromagnetic four-way pilot valve 80 is connected to the four ports 14 (intake side low pressure port S).

  The structure of the four-way pilot valve 80 is well known, and as shown in FIG. 22, opposite to the main body 50 of the actuator 7 on the lower surface side of the lower valve seat 10B of the main valve housing 10. A cylindrical valve case part 81 having a lower surface opened downward to the side and a solenoid fixed by brazing, caulking or the like so as to airtightly seal the lower surface opening of the valve case part 81 And a bottomed cylindrical valve seat block 83 having an inner end face as a valve seat (seat surface) 92 airtightly attached to the side surface of the valve case 81 by press-fitting, caulking or the like. Have.

  The inside of the valve case portion 81 is a valve chamber 88, and the valve chamber 88 communicates with the inside of the main valve housing 10, which is a high pressure portion, through a pore 89 formed in the lower valve seat 10B. It has become. The solenoid section 82 includes a coil 82a for energization and excitation, a cover case 82b covering the outer periphery of the coil 82a, a suction element 84 disposed on the inner peripheral side of the coil 82a and fixed to the cover case 82b by a bolt 82c A plunger 85 or the like disposed opposite to the child 84 is provided. The plunger 85 is slidably fitted in a cylindrical guide pipe 86 whose lower portion is disposed between the coil 82 a and the suction element 84. The lower end of the guide pipe 86 is fixed to the outer peripheral terrace portion of the suction element 84 by welding or the like, and the upper end flange portion is airtightly attached to the valve case portion 81 by welding, brazing, caulking or the like.

  In addition, a compression coil spring 87 is compressed between the suction element 84 and the plunger 85 to bias the plunger 85 in a direction away from the suction element 84 (upward in the figure).

  At the end opposite to the suction element 84 side of the plunger 85, the valve body holder 90 for holding the valve body 91 slidably in the thickness direction at the free end side is press-fitted with the mounting tool 96 at its base end.・ Fixed by caulking etc. A leaf spring 94 is attached to the valve body holder 90 for biasing the valve body 91 in a direction (thickness direction) to press the valve seat 92. The valve body 91 slides on the seat surface of the valve seat 92 as the plunger 85 moves up and down.

  The valve seat 92 is provided with a port a, a port b, and a port c in order from the top, and the valve body 91 is made to selectively communicate the port a with the port b and the port b with the port c. A recessed portion 93 recessed in the thickness direction is provided. In the valve seat block 83, one end of the thin tube 95a communicates with only the port a, and one end of the thin tube 95b communicates with only the port b so as to communicate only with the port b. Are attached airtightly.

  The other end of the thin tube 95a is connected to the working chamber upper portion 55A through the upper port 56 of the main body 50, and the other end of the thin tube 95b is connected to the fourth port 14 (intake side low pressure port S) which is a low pressure portion. The other end of the thin tube 95c is connected to the lower portion 55B of the operation chamber via the lower port 57 of the main body 50.

  In the four-way pilot valve 80 configured as above, when the solenoid unit 82 is deenergized, as shown in FIG. 22A, the plunger 85 has its upper end valve operated by the biasing force of the compression coil spring 87. The seat block 83 is pushed up to a position in contact with the seat block 83. In this state, the valve body 91 is located on the port a and the port b, and the recess 93 communicates the port a and the port b, and the port c and the valve chamber 88 communicate with each other. The high pressure fluid is introduced into the lower portion 55B via the small hole 89 → valve chamber 88 → port c → capillary 95c → lower port 57, and the high pressure fluid in the upper portion 55A of the working chamber is upper port 56 → capillary 95a → port a → recessed portion 93 → port b → thin tube 95 b → flow to the fourth port 14 (suction side low pressure port S) and discharged.

  On the other hand, when the solenoid unit 82 is turned on, the plunger 85 is drawn to the position where the lower end thereof contacts the suction member 84 by the suction force of the suction member 84, as shown in FIG. . At this time, the valve body 91 is located on the port b and the port c, and the recess 93 makes the port b and the port c communicate with each other, and the port a and the valve chamber 88 communicate with each other. The fluid is introduced into the upper portion 55A of the working chamber via the small hole 89 → valve chamber 88 → port a → capillary 95a → upper port 56, and the high pressure fluid in the lower portion 55B of the working chamber is lower port 57 → capillary 95c → port c → The fluid flows from the concave portion 93 → the port b → the thin tube 95 b → the fourth port 14 (the suction side low pressure port S) and is discharged.

  Therefore, when the energization to the solenoid portion 82 is turned off, the upper moving stroke is taken, the main valve body 20 is rotated from the second rotational position to the first rotational position, and the flow path switching as described above is performed. On the other hand, when energization to the solenoid portion 82 is turned on, the downward movement stroke is taken, and the main valve body 20 rotates from the first rotational position to the second rotational position, and the flow path as described above A switch is made.

  As described above, in the flow path switching valve 1 of the present embodiment, the differential pressure between the high pressure fluid and the low pressure fluid flowing through the main valve 10 is switched by switching the energization of the electromagnetic four-way pilot valve 80 ON / OFF. Since the main valve body 20 is turned using the above, it is possible to reduce the cost, the power consumption, and the energy saving as compared with the case where the main valve body 20 is turned by the electric motor or the like. Can. In addition, the flow-path switching by the actuator 7 of a present Example can be performed more rapidly than the flow-path switching performed with an electric motor + reduction gear.

  Further, the actuator 7 for rotating the main valve body 20 moves the pressure receiving moving body 60 up and down by fluid pressure, converts this up and down movement into rotational movement, and transmits it to the main valve body 20. A portion that receives high pressure as compared to a plate-like body with a large pressure receiving area with respect to the plate thickness, where a portion that receives high pressure like this is cantilevered on the extension shaft portion of the rotary shaft portion of the main valve body Since sufficient strength can be secured and durability can be improved in (the pressure receiving moving body 60), the pressure receiving area can be enlarged because sufficient strength can be secured, and therefore, the flow path switching can be performed reliably and quickly. be able to.

  In addition to the above, a ball screw mechanism is generally known as a mechanism for converting linear motion into rotational motion, but a normal ball screw mechanism uses a large number of balls and a return structure is also required. Compared with the motion conversion mechanism 58 of the example, the structure is complicated and expensive, and use in a high temperature and high pressure environment is not considered. Is difficult. On the other hand, the hydraulic actuator provided with the motion conversion mechanism 58 of the present embodiment has an extremely simple structure with a small number of parts, which is advantageous in cost and measures when used under high temperature and high pressure environment (The thickness of the pressure receiving moving body 60 can be increased, for example.) Therefore, the flow path switching valve 1 of this embodiment is a flow which is incorporated particularly in a high temperature and high pressure environment such as a heat pump type cooling and heating system. It will be extremely cost effective as a path switching valve.

[Modification of actuator]
FIG. 23 shows a modification of the actuator. The basic configuration of the actuator 8 in the illustrated example is the same as that of the actuator 7, the main body 50, the motion conversion mechanism 58 (the pressure receiving moving body 60, the rotational driving body 65, the ball 72, the housing 74, the spiral groove 75), the upper port 56, the lower port 57, the four-way pilot valve 80, etc. (the symbols are common), but in the actuator 8 of this example, the drive shaft portion of the rotary drive 65 and the rotation shaft portion of the main valve body 20 are common. The main valve body 20 and the rotational drive body 65 are integrally pivoted so as to be disposed on the axis.

  Specifically, the rotary drive 65 is externally fitted and fixed to the lower rotary shaft portion 30B of the main valve body 20 by press fitting, caulking or the like, and the rotation of the rotary drive body 65 is directly transmitted to the main valve body 20 It has become. Therefore, in the second embodiment, the rotation transmission mechanism 77 of the actuator 7 is unnecessary, and the upward movement of the pressure receiving moving body 60 is stopped by the lower surface 10 e of the lower valve seat 10 B. The upper surface closing member 53 is also unnecessary. Therefore, the configuration is simplified, which is advantageous in cost.

  Of course, the flow path switching valve according to the present invention can be incorporated not only into the heat pump type cooling and heating system but also into other systems, devices and devices.

  Moreover, although aluminum, stainless steel, etc. are used as materials for the valve housing 10, the main valve body 20, the pressure receiving moving body 60, the rotary driving body 65, etc., it is not limited thereto, and other metals, resins, etc. Any material that can withstand the pressure of the fluid to be introduced may be used.

DESCRIPTION OF SYMBOLS 1 flow-path switching valve 5 main valve 7 actuator 10 main valve housing 10A upper side valve seat 10B lower side valve seat 11 1st port 12 2nd port 13 3rd port 14 4th port 17 seat surface 20 main valve body 20A upper half part 20B lower half portion 21 first layer member 22 second layer member 23 third layer member 24 fourth layer member 27 cross groove 29 compression coil spring 30A upper side rotational shaft portion 30B lower side rotational shaft portion 31 first communication passage 32 second Communication passage 33 Third communication passage 34 Fourth communication passage 36 Convex part 37 Seal surface 41 First communication passage 42 Second communication passage 43 Third communication passage 44 Fourth communication passage 45 Ball type seal surface separation mechanism 50 Main body (Actuator )
52 lower surface closing member 53 upper surface closing member 54 key groove 55 operation chamber 55A operation chamber upper portion 55B operation chamber lower portion 56 upper port 57 lower port 58 motion conversion mechanism 60 pressure receiving moving member 62 packing 63 operating pin 65 rotation driver 72 ball 75 spiral groove 76 Rotation drive shaft 77 Rotation transmission mechanism 80 Four-way pilot valve 82 Solenoid part 83 Valve seat block 85 Plunger 88 Valve chamber 89 Pore 90 Valve body holder 91 Valve body 92 Valve seat 93 Recesses a, b, c Ports (four-way pilot valve )
95a, 95b, 95c Tubular D Discharge-side high-pressure port S Intake-side low-pressure port C Room-side inlet / outlet port E Room-side inlet / outlet port

Claims (10)

A cylindrical main valve housing whose opening is hermetically sealed by a valve sheet, at least three ports provided in the valve sheet, and a main valve body rotatably disposed in the main valve housing A main valve having a pressure sensor, biasing means for biasing the main valve body toward the valve seat, and an actuator for rotating the main valve body.
The main valve body is provided with a plurality of communication paths for selectively communicating between the ports, and by rotating the main valve body, the communication ports are switched.
Between the main valve body and the valve seat, there is provided a ball type seal surface separating mechanism for separating the seal surface on the main valve body side from the valve seat when the main valve body is rotating. Flow path switching valve.   At least one first communication passage capable of communicating at least one of the ports and another one of the ports, and at least one communication capable of communicating one of the ports with another one in the main valve body A second communication passage is provided, and by rotating the main valve body in one direction, switching of the flow passage from between ports communicated by the first communication passage to between ports communicated by the second communication passage is performed. And switching the flow path from between the ports communicated by the second communication passage to the port communicated by the first communication passage by rotating the main valve body in the other direction after the flow passage switching. The flow control valve according to claim 1, characterized in that   The flow path switching valve according to claim 1 or 2, wherein at least one of the plurality of communication paths is formed of a U-shaped passage.   The convex part which has an annular sealing surface closely contacting the opening of each said port in the said valve seat is protrudingly provided by the edge part of the said communicating path, The any one of Claim 1 to 3 characterized by the above-mentioned. Flow path switching valve as described.   The ball type seal surface separation mechanism includes: a ball; a housing portion for housing the ball in a state in which a portion of the ball is projected in the up and down direction; Before the start of rotation of the valve body and at the time of the end of rotation, a part of the ball protruding from the accommodation portion is fitted so that the seal surface on the main valve body side does not separate from the valve seat. When the body rotates, the ball and the housing portion have the same circumferential shape as the ball rolls up while pushing up or pushing down the main valve body, and the ball and the housing portion have the same circumference of the main valve body. The concave hole is provided at two or more locations on the same circumference of the valve seat, at the same position as the accommodation portion in plan view, and from the position, the main valve body is angularly separated from the position when the main valve is switched. Provided at Flow path switching valve according to claim 1, any one of 4, wherein Rukoto.   The actuator has a main body portion provided with a working chamber into which high pressure fluid supplied to the main valve is introduced, and the pressure of the high pressure fluid is used in the working chamber to reverse reciprocating linear motion. The flow control valve according to any one of claims 1 to 5, wherein a motion conversion mechanism is provided to convert rotational motion in both directions. The motion converting mechanism is configured to receive the pressure receiving body housed in the working chamber so as to be capable of moving up and down in a state in which the rotation is blocked, and the pressure receiving body so as to be relatively rotatable corresponding to the vertical movement of the pressure receiving body. And a rotary drive which is interpolated or extrapolated to the moving body,
A packing is provided on the outer periphery of the pressure receiving moving body for sealing the space between the pressure chamber and the inner circumferential surface of the working chamber in an airtight manner to divide the working chamber into an upper portion and a lower portion of variable volume. An upper port for introducing and discharging high pressure fluid is provided in the upper part of the working chamber, and a lower port for introducing and discharging high pressure fluid is provided in the lower part of the working chamber. Flow path switching valve as described.   The actuator introduces the high pressure fluid into the lower part of the working chamber through the lower port, and discharges the high pressure fluid from the upper part of the working chamber through the upper port to move the pressure receiving movable body upward. An upper moving stroke for rotating the rotary driving body in one direction, introducing a high pressure fluid into the upper portion of the working chamber through the upper port, and discharging a high pressure fluid from the lower portion of the working chamber through the lower port. 8. The flow path switching according to claim 7, characterized in that the pressure receiving moving body can be moved downward to selectively take a lower moving stroke for rotating the rotational driving body in the other direction. valve.   The switching between the upper and lower moving strokes is performed by a four-way pilot valve connected to the upper port and the lower port, and the high pressure portion and the low pressure portion of the main valve. The flow passage switching valve according to claim 8, characterized in that:   The flow passage switching valve according to claim 9, wherein the main body of the actuator and the four-way pilot valve are provided on the upper surface side of the upper valve seat or on the lower surface side of the lower valve seat.

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