JP6689418B2 - Flow path switching valve - Google Patents

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 or the like.

  Generally, a heat pump type cooling / heating system for a room air conditioner, a car air conditioner, etc., includes a flow path switching valve as a flow path (flow direction) switching means in addition to a compressor, an outdoor heat exchanger, an indoor heat exchanger, an expansion valve, etc. Is equipped with.

  An example of the heat pump type cooling and heating system provided with this flow path switching valve will be briefly described with reference to FIG. The heat pump type cooling and heating system 100 of the illustrated example is configured such that the switching of the operation modes (cooling operation and heating operation) is performed 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 are provided, and four ports are provided 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 inlet / outlet port C, the indoor-side inlet / outlet port E, and the suction-side low-pressure port S is arranged.

  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, as shown by a solid arrow in FIG. 24, the discharge side of the flow path switching valve 140 is shown. The high pressure port D is communicated with the outdoor side inlet / outlet port C, and the indoor side inlet / outlet port E is communicated with the suction side low pressure port S. As a result, the refrigerant is sucked into the compressor 110, and the high-temperature and high-pressure refrigerant is guided from the compressor 110 to the outdoor heat exchanger 120 via the flow path switching valve 140, where it is heat-exchanged with the outdoor air and condensed. Then, the 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 indoor heat exchanger 130, where it heat-exchanges (cools) with indoor air to evaporate, 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 becomes the indoor side inlet / outlet port E and the outdoor side inlet / outlet port C becomes The high-pressure and high-pressure refrigerant is introduced from the compressor 110 to the indoor heat exchanger 130 by being communicated with the low-pressure ports S on the suction side, where it is heat-exchanged (heated) with the indoor air and condensed to become a high-pressure two-phase refrigerant. And 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 to evaporate, and from the outdoor heat exchanger 120, low temperature and low pressure. Is returned to the suction side of the compressor 110 via the flow path switching valve 140.

  As a four-way switching valve incorporated in a heat pump type cooling and heating system as described above, there is conventionally known one provided with a valve body (valve housing) having a slide type main valve element built therein and an electromagnetic pilot valve ( See, for example, Patent Document 1. The flow path switching valve disclosed in Patent Document 1 has a discharge housing high-pressure port D, an outdoor-side inlet / outlet port C, an intake-side low-pressure port S, and an indoor-side inlet / outlet port E formed in the valve housing. A slide type main valve element is arranged so as to be slidable in the left-right direction in order to create a communication state of the ports D → C and E → S or the ports D → E and C → S (switch the flow paths). . The high pressure refrigerant on the compressor discharge side and the low pressure refrigerant on the compressor suction side are introduced to the left and right of the slide type main valve element in the valve housing through a pilot valve. The high pressure chamber and the low pressure chamber defined by the piston type packing of the above are provided, and the slide type main valve element is slid in the left and right direction by utilizing the pressure difference between the high pressure chamber and the low pressure chamber to switch the flow path. Is to be done.

  On the other hand, Patent Document 2 proposes a rotary four-way switching valve including a pilot valve. This four-way switching valve divides the inside of the cylindrical body (main valve housing) into two by a partition (a plate-shaped main valve body that is cantilevered on the rotating shaft), and at the outer periphery of the main valve housing. The discharge-side high-pressure port D and the suction-side low-pressure port S, and the outdoor-side inlet / outlet port C and the indoor-side inlet / outlet port E are arranged to face each other by about 180 °, and the plate-shaped main valve body is rotated. Thus, the flow paths are switched, that is, 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, respectively, and the discharge-side high-pressure port D. To the indoor side inlet / outlet port E, and the outdoor side inlet / outlet port C to the second communication state in which they communicate with the suction side low pressure port S, respectively, and rotation of the main valve body (flow path switching) Installed above the main valve housing The fluid pressure actuator that utilizes the differential pressure between the high-pressure refrigerant and the low-pressure refrigerant in the system (two separated by a plate-shaped body that is cantilevered on the extension shaft of the rotary shaft of the plate-shaped main valve body) This is done by selectively introducing and discharging high-pressure refrigerant to the working chamber) with a pilot valve.

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

  The conventional flow path switching valve as described above has the following problems to be solved.

  That is, in the slide type flow path switching valve disclosed in Patent Document 1, the high-pressure fluid (refrigerant) collides with the inner wall surface or the like in the valve housing having a relatively small internal volume, and the flow direction thereof largely changes. There is a tendency to increase the pressure loss, and the sliding main valve body with a pair of left and right piston type packings slides to switch the flow path, so the sliding parts are easily worn by stick slips, etc. Along with this, there is also a problem that the sealing property of the sliding portion deteriorates and the valve easily leaks.

  Further, in the rotary type flow path switching valve disclosed in Patent Document 2, since the main valve body that receives high pressure is supported in a cantilever manner and is a plate-shaped body having a large pressure receiving area with respect to the plate thickness, it is deformed ( (Flexure) is likely to occur, and there is a problem in strength and durability, and since the surface to be sealed contains a cylindrical surface, the above-mentioned deformation (deflection) is likely to occur and the sealing performance is likely to be impaired. There is also a problem that the valve may leak easily.

  In addition, the high-pressure fluid collides with the plate-shaped valve element and the inner wall surface in the valve housing, and the flow direction changes greatly, resulting in a large pressure loss, and also at approximately 90 ° intervals at the four outer circumferences of the main valve housing. Since the port is provided in, there is also a problem that the arrangement of the piping is troublesome and 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 heat pump type cooling and heating system described above, in the main valve housing, the high temperature high pressure refrigerant and the low temperature low pressure refrigerant are in close proximity (thin wall Since they are flowed in a state where they are separated from each other, there is a problem that the amount of heat exchange in the main valve housing becomes large and the efficiency of the system deteriorates.

  In addition, in the flow path switching valve disclosed in Patent Document 2, even in the fluid pressure type actuator for rotating the main valve body (flow path switching), there is a portion that receives high pressure as in the main valve body side. The plate-shaped main valve is cantilevered by the extension shaft of the rotary shaft of the plate-shaped main valve and has a large pressure receiving area with respect to the plate thickness, so deformation (deflection) is likely to occur and strength and durability There's a problem.

  The present invention has been made in view of the above circumstances, and an object thereof is to reduce pressure loss and wear of sliding parts as much as possible, improve sealability, and prevent valve leakage. (EN) Provided is a flow path switching valve which can be made difficult, can secure sufficient strength to withstand high pressure and can improve durability, and can also be convenient for manipulating pipes, reducing 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 in which a high-temperature high-pressure fluid and a low-temperature low-pressure fluid are flowed, such as a heat pump type cooling and heating system. It is to provide a flow path switching valve adapted to obtain.

In order to achieve the above-mentioned object, the flow path switching valve according to the present invention is basically a tubular main valve whose upper opening and lower opening are hermetically sealed by an upper valve seat and a lower valve seat. A main valve having a valve housing, a total of at least three ports provided on the upper valve seat and / or the lower valve seat, and a main valve body rotatably disposed in the main valve housing; An actuator for rotating the main valve body, a plurality of communication passages for selectively communicating between the ports are provided in the main valve body, and by rotating the main valve body, , The communicating ports are switched, and the main valve body is divided into two parts, that is, an upper half part and a lower half part that are integrally rotatable and can move up and down. parts, respectively have a U-shaped communication passage, and the upper half An urging means for urging them in mutually opposite directions is interposed between the lower half portion and the lower half portion, and as one of the communication passages, a split extending across the upper half portion and the lower half portion. A cylindrical portion having a communication passage, wherein a large diameter portion is formed on one of a lower end portion of an upper half portion and an upper end portion of a lower half portion of the divided communication passage and the other portion is inserted into the large diameter portion. There are extended, O-ring is characterized that you have been interposed between the large diameter portion and said cylindrical portion.

  In a preferred specific embodiment, at least one first communication passage capable of communicating at least one of the ports and another one in the main valve body, and one of the ports and another one And at least one second communication passage that can communicate with each other are provided, and by rotating the main valve element in one direction, between the ports communicated with the first communication passage from the ports communicated with the second communication passage. To the port communicating with the second communication passage by rotating the main valve element in the other direction after switching the flow passage to the port communicating with the first communication passage. The switching of the flow paths is performed.

  In another preferred specific embodiment, the upper valve seat and / or the lower valve seat are provided with first, second, third and fourth ports, and the main valve body is provided with the main valve body. When taking the first rotational position, the first communication passage that communicates the first port and the third port, the second communication passage that communicates the second port and the fourth port, and the main valve body A third communication passage that communicates the first port with the second port or the fourth port and a fourth communication passage that communicates the third port with the fourth port or the second port when the rotation position of 2 is taken. Is provided.

  In this case, in a preferred mode, the upper valve seat is provided with first and second ports, and the lower valve seat is provided with third and fourth ports.

  In a preferred aspect, at least one of the plurality of communication passages is formed of a linear passage as a whole.

  At both ends of the communication passage, preferably, a protrusion having an annular sealing surface that closely contacts around the opening of each port in the upper valve seat and / or the lower valve seat is provided in a protruding manner.

  In another preferred aspect, between the main valve body and the upper valve seat and between the main valve body and the lower valve seat, at the time of rotation of the main valve body, a sealing surface on the main valve body side. A ball-type seal surface separating mechanism for separating the upper valve seat and the lower valve seat from each other is provided.

  In a further preferred embodiment, the ball-type seal surface separating mechanism houses a ball and the ball in a state in which a part of the ball is projected in the vertical direction, rotatably and substantially in the state of being prevented from moving. Of the main valve body before the start of rotation and at the end of rotation of the main valve body, so that the sealing surface on the main valve body side does not separate from the upper valve seat and the lower valve seat. When a part of the ball is fitted and the main valve body is rotated, the ball pushes down the upper half portion, and a concave hole having a size and shape that rolls out while pushing up the lower half portion, The ball and the accommodating part are provided at two or more locations on the same circumference of the upper half part and the lower half part, and the recessed hole has the same circumference of the upper valve seat and the lower valve seat. Top view It said main valve body from the same position and the position and the accommodation portion is provided in the angle component away rotating the flow channel switching.

  In another preferred aspect, the actuator has a main body portion in which a working chamber into which high-pressure fluid supplied to the main valve is introduced is provided, and the working chamber uses the pressure of the high-pressure fluid, A motion conversion mechanism for converting the reciprocating linear motion into a rotational motion in both forward and reverse directions is provided.

  In a preferred embodiment of the flow path switching valve according to the present invention, for example, two of the four communication passages that communicate between the ports have a thickness (passage diameter) from the start end to the end that is equal to the diameter of each port. The passages are formed in substantially the same straight line, and the refrigerant flows straight from below or above the port, so that there is almost no pressure loss in the main valve (main valve body). Further, since the inner volume of the remaining communication passages can be made relatively large, the pressure loss can be reduced, and in total, the pressure loss can be considerably reduced as compared with the conventional flow path switching valve.

  Further, the main valve body has a two-part configuration of an upper half part and a lower half part, and the upper half part and the lower half part can be moved up and down independently of each other, and the upper half part and the lower half part are Since the urging means is interposed between the upper and the lower half, the upper half is pushed up by the urging force to press the sealing surface around each port on the valve seat surface of the upper valve seat, and the lower half is It is depressed so that its sealing surface is pressed around each port on the valve seat surface of the lower valve seat. In this case, since the convex portion is provided on the main valve body (upper half portion and lower half portion) side and the end surface is the annular seal surface, the area of the portion that contacts the valve seat surface is the minimum necessary. Therefore, the contact surface pressure is increased. As a result, 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 plates, the valve seat surface can be made flat and smooth (the surface accuracy can be easily increased). The sealability can be significantly improved as compared with the case where the surface to be sealed includes a cylindrical surface.

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

  In addition, the ball-type seal face separation mechanism allows the upper half of the main valve to be pushed down and the lower half to be pushed up when the main valve is rotating (during flow path 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, and therefore stick-slip or the like is less likely to occur and sliding parts The wear can be significantly suppressed, and further, the wear is suppressed, so that the sealability is improved and the valve leakage can be effectively suppressed.

  Further, in the flow path switching valve of the present invention, the main valve body (upper half portion and lower half portion) that receives high pressure can be formed into a cylindrical shape, and the communication passage can be provided inside the main valve body, so that it can be modified as in the conventional example. (Bending) hardly occurs, 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 in which a high-temperature high-pressure refrigerant and a low-temperature low-pressure refrigerant flow, such as a heat pump type cooling and heating system, the communication passages are relatively separated from each other in the main valve body. Since they are installed separately, heat exchange in the main valve housing is higher than that of the conventional type in which high-temperature and high-pressure refrigerant and low-temperature and low-pressure refrigerant flow close to each other (a thin wall is separated). The amount can be significantly reduced, and the system efficiency can be improved.

  Problems, configurations, and effects other than those described above will be clarified by the following embodiments.

(A) is a side view of the first embodiment of the flow path switching valve according to the present invention, (B) is a top side layout view of the flow path switching valve shown in (A), and (C) is ( The lower surface side layout drawing of the flow-path switching valve shown by A). The other side view which partially fractured | ruptured according to the AA arrow line of FIG. 1 (B). The other side view which partially fractured | ruptured 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. 3 is an enlarged cross-sectional view for explaining the configuration and operation of a seal surface separating mechanism provided in the flow path 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 top layout view, (2) is XX of (1). A sectional view taken along the line of view of the arrow, (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 top side layout drawing, and (2) is ( Sectional drawing which follows the XX arrow line 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 rotation position, (1) is a plan view, (2) is a line XX line of view of (1). FIG. 3B is a cross-sectional view according to FIG. 1B, showing the state in which the first layer member of the main valve body in the first embodiment is in the second rotation position, FIG. 1A is a plan view, and FIG. -A sectional view taken along the line X. (A) shows a state in which the second layer member of the main valve body in the first embodiment is in the first rotation position, (1) is a plan view, (2) is a line XX arrow of (1). 2B is a cross-sectional view according to FIG. 1B, showing 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 X in (1). -A sectional view taken along the line X. (A) shows a state in which the third layer member of the main valve body in the first embodiment is in the first rotation position, (1) is a plan view, (2) is a view taken along line XX of (1). 3B is a cross-sectional view according to FIG. 1B, in which the third 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 X in (1). -A sectional view taken along the line X. (A) shows the state in which the fourth layer member of the main valve body in the first embodiment is in the first rotation position, (1) is a plan view, (2) is the line XX of (1). 2B is a cross-sectional view according to FIG. 1B, showing a state in which the fourth layer member of the main valve body of the first embodiment is in the second rotation position, (1) is a plan view, and (2) is X in (1). -A sectional view taken along the line X. The example which made the upper half part and the lower half part of the main valve body of 1st Example into each one thing is shown, (A) is a state in a 1st rotation position, (B) is a 2nd rotation position. Sectional drawing which shows each state. The example which made the upper half part and the lower half part of the main valve body of 1st Example into one is shown, (A) is a state in a 1st rotation position, (B) is a state in a 2nd rotation position Sectional drawing which respectively shows. The flow-path switching valve of 2nd Example is shown, (A) shows the state which a main valve body is in a 1st rotation position, (B) rotates a main valve body 90 degrees clockwise from a 1st rotation position. In the state of the second rotation position, (1) is a layout view on the upper surface side, (2) is a schematic view showing a communication passage configuration in each state, and (3) is a layout view on the lower surface side. (A) shows (1) 1st layer member, (2) 2nd layer member, (3) 3rd layer member, (4) in the state where the main valve body in 2nd Example exists in a 1st rotation position. ) Each of the 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 rotation position, and (1) to (4) of (B) are (A). (1) to (4) of FIG. (A) shows (1) 1st layer member, (2) 2nd layer member, (3) 3rd layer member, (4) in the state where the main valve body in a 2nd Example is in a 2nd rotation position. ) Each of the plan views of the fourth layer member, (B) shows the communication passage configuration in the state where the main valve body is in the second rotational position, and the upper and lower stages of (1) of (B) are: U-U arrow line in (1) of (A), partial sectional view which follows VV arrow line, respectively, (2) and (3) of (B) of (2) and (3) of (A). Sectional drawing which follows the YY arrow line, (4) upper-stage side of (B), and a lower side are partial cross-sectional views which follow the JJ arrow line and KK arrow line in (4) of (A), respectively. The flow-path switching valve of 3rd Example is shown, (A) is a state in which a main valve body is in a 1st rotation position, (B) is a state in which a main valve body is in a 2nd rotation position, (1) ) Is a layout view on the upper surface side, and (2) is a cross-sectional view taken along the line XX of (1). FIG. 3 is a partially cutaway enlarged view of a lower portion of FIG. 2 showing an actuator portion in the first embodiment of the flow path switching valve according to the present invention. 17A is a partially enlarged cross-sectional view showing the main part of the actuator shown in FIG. 17, and FIG. 18B is an exploded perspective view of the main part of the motion conversion mechanism shown in FIG. FIG. 18 is a schematic configuration diagram showing an example of a rotation transmission mechanism used in the actuator shown in FIG. 17. FIG. 18 is a schematic configuration diagram showing another example of the rotation transmission mechanism used in the actuator shown in FIG. 17. FIG. 18 is a diagram which is used for describing an operation of the actuator shown in FIG. 17. FIG. 18 is an enlarged cross-sectional view showing a four-way pilot valve provided in the actuator shown in FIG. 17, (A) showing when energization is OFF and (B) showing when energization is ON. The partial notch enlarged view which shows the other Example of the flow-path switching valve which concerns on this invention. The schematic block diagram which shows an example of a heat pump type cooling and heating system.

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

  1A and 1B show a first embodiment of a flow path switching valve according to the present invention. FIG. 1A is a side view, FIG. 1B is a top side layout view, and FIG. 1C is a bottom side layout view. In addition, FIGS. 2, 3, and 4 are other side views partially broken along the line AA of FIG. 1B, other side views partially broken along the line BB, and C, respectively. FIG. 7 is an enlarged cross-sectional view of the main valve portion taken along the line C of FIG.

  In the present specification, the description of the position and direction such as up and down, left and right, and front and back is added for convenience according to the drawings in order to avoid complicated explanation, and is actually incorporated in a heat pump type cooling and heating system or the like. It does not necessarily indicate the position and direction in the closed state.

  Further, in each drawing, the gaps formed between the members and the separation distances between the members are larger than the dimensions of the respective constituent members for the sake of easy understanding of the invention and convenience of drawing. Or it may be drawn small.

[First embodiment of main valve]
The flow path switching valve 1 of the illustrated embodiment is a four-way switching valve, and is used as, for example, the four-way switching valve 140 in the heat pump type cooling and heating system 100 shown in FIG. 24 described above. And a pressure type 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 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 fixed by caulking so as to hermetically seal the cylindrical body portion 10C and the upper opening of the body portion 10C, and further soldering and brazing. A thick disc-shaped upper valve seat 10A fixed by welding, etc., and a thick disc fixed to the body 10C in the same manner as the upper valve seat 10A so as to close the lower surface opening of the body 10C. A lower valve seat 10B, and a first port 11 and a second port 12 made of pipe joints are vertically provided on the left and right of the upper valve seat 10A, and a pipe is provided on the left and right of the lower valve seat 10B. A third port 13 and a fourth port 14 which are 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 arranged 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 the present embodiment, when incorporated in the heat pump type cooling and heating system 100 as shown in FIG. 24, for example, the first port 11 is the discharge side high pressure port D connected to the compressor discharge side and the second port. 12 is an indoor-side inlet / outlet port E connected to the indoor heat exchanger, 3rd port 13 is an outdoor-side inlet / outlet port C connected to the outdoor heat exchanger, and 4th port 14 is connected to the compressor suction side. The low pressure port S on the suction side is provided (see FIG. 1).

  A bearing hole 15A for rotatably supporting an upper rotary shaft portion 30A (described later) of the main valve body 20 is provided in the center of 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). Is provided in the lower valve seat 10 </ b> B near the center on the lower surface side, and a recess 19 (accommodating portion of the rotation transmission mechanism 70 described later) is provided downward. A bearing hole 15B that rotatably supports a lower rotary shaft portion 30B (described later) of the valve body 20 is provided.

  Further, the main body 50 of the actuator 7 and the pilot valve 80 are provided in front of and behind the lower surface of the lower valve seat 10B. The main body 50 and the pilot valve 80 are configured so as not to project laterally from the main valve housing 10 in a plan view (contained within the diameter of the lower valve seat 10B).

  The main valve body 20 has a two-part configuration of an upper half portion 20A and a lower half portion 20B having a short cylindrical shape. Specifically, the upper half portion 20A is configured 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, and has a thick wall. The lower half portion 20B is composed of the disk-shaped third layer member 23 and the 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 of the lower half portion) and the lower half portion 20B (the third layer member 23 of the lower half portion 20B), four compressions as biasing means for biasing them in mutually opposite directions. The coil spring 29 is compressed (see FIG. 2). The four compression coil springs 29 have four spring accommodating holes 23h (see FIG. 9) provided on the same circumference on the upper surface side of the third layer member 23 at equal angular intervals, and part of the springs upward. It is loaded in a protruding state.

  A rectangular cross section passing through the center line O of the main valve body 20 (common to the main valve housing 10) at the same position in plan view on the upper surface side of the first layer member 21 and the lower surface side of the fourth layer member 24 of the main valve body 20. Crossing grooves 27, 27 of the main valve body 20 are formed in the vicinity of both ends of the crossing grooves 27, 27 so as to be integrally rotatable and vertically movable. Therefore, as shown in FIG. 3, two through-holes 26 are formed, and the stepped integrated rotary rod 25 having the small diameter portions 25a at the upper and lower ends is inserted into the two through-holes 26. Has been done.

  As shown in FIGS. 2 to 4, the rotary shaft portion of the main valve body 20 has an upper rotary shaft portion 30A that can behave integrally with the main body portion (upper half portion 20A, lower half portion 20B) of the main valve body 20. And the lower rotary shaft portion 30B. The upper rotary shaft portion 30A includes a pivot shaft portion 30a inserted into the bearing hole 15A and a square rod portion 30b having a rectangular cross section that fits into the transverse groove 27. The lower rotary shaft portion 30B includes a pivot portion 30c inserted into the bearing hole 15B, a rectangular rod portion 30d having a rectangular cross section that fits 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 ends of the integral rotation rod 25 are fitted into the insertion holes, thereby allowing the integral rotation. The rod 25 is fixed to the upper rotary shaft portion 30A and the lower rotary shaft portion 30B.

  Therefore, the upper and lower rotary shaft portions 30A and 30B and the left and right integrally rotatable rods 25 and 25 form a frame-shaped body 28 assembled in a well shape or a rectangular shape so as to be relatively movable and rotatable integrally with each other. Therefore, the frame-shaped body 28 can flexibly cope with the vertical movement, inclination, positional displacement, etc. of the main valve body 20 (upper half portion 20A, lower half portion 20B) having a two-part configuration.

  In switching the flow path, the main valve body 20 is rotated in both forward and reverse directions by an actuator 7 described later, and a first rotational position as shown in FIG. The second rotation position as shown in FIG. 6B, which is rotated clockwise by 60 °, can be selectively set.

  The main valve body 20 has a first communication passage 31 that communicates the first port 11 and the third port 13 and a second communication passage that communicates the second port 12 and the fourth port 14 when taking the first rotational position. A communication passage 32 is provided, and when the second rotation position is taken, a third communication passage 33 that connects the first port 11 and the second port 12 and a third port 13 and the fourth port 14 are connected. A fourth communication passage 34 is provided.

  Specifically, the upper surface opening or the lower surface opening of each of the passage portions 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. 11 to 14 are arranged on the same circumference, and the diameters thereof are substantially the same as the diameters of the respective ports 11 to 14, and further, the first communication passage 31 and the second communication passage 32 are provided in the respective ports. The passage diameter is substantially the same as the diameters of 11 to 14.

  As shown in FIG. 7, the first layer member 21 that constitutes the upper portion of the main valve body upper half portion 20A is provided with two linear through passage portions 21A and 21B at 180 ° intervals, and at the same time, the second Two passage portions 21C and 21D with horizontal holes, which are closed by the layer member 22 and whose lower surface openings are closed, are connected by the horizontal holes 21E having a corrugated plan view. The lateral holed passage portions 21C and 21D are arranged at an interval of 180 °, and the two are combined to form a U-shaped communication passage (third communication passage 33) having a relatively large volume. The angular interval between the straight through passage portions 21A, 21B and the passage portions 21C, 21D with lateral holes is 60 °.

  Therefore, when the main valve body 20 is in the first rotation position, the straight through passage portions 21A and 21B are located directly below the first port 11 and the second port 12, and the main valve body 20 is moved from the first rotation position. When rotated clockwise by 60 °, the upper surface openings of the straight through passage portions 21A, 21B are closed by the upper valve seat 10A, and the upper surface openings of the passage portions 21C, 21D with lateral holes are formed by the first port 11 and the second port 12. Located just below.

  As shown in FIG. 8, the second layer member 22 forming the lower portion of the main valve body upper half portion 20A is provided with two straight through passage portions 22A and 22B at 180 ° intervals. The straight line passage portions 22A and 22B are located directly below the straight line passage portions 21A and 21B of the first layer member 21.

  As shown in FIG. 9, the third layer member 23, which constitutes the upper portion of the lower half portion 20B of the main valve body, is provided with two linear through passage portions 23A and 23B at 180 ° intervals. The straight line passage portions 23A and 23B are located directly below the straight line passage portions 22A and 22B of the second layer member 22.

  As shown in FIG. 10, the fourth layer member 24 forming the lower part of the main valve body lower half portion 20B has two linear through passage portions 24A at 180 ° intervals as in the case of the first layer member 21. , 24B are provided, and two lateral hole-equipped passage portions 24C, 24D connected by lateral holes 24E having a corrugated plan view are provided, the upper surface opening of which is closed by the third layer member 23. The straight line passage portions 24A and 24B are located directly below the straight line passage portions 23A and 23B of the third layer member 23. The lateral hole-provided passage portions 24C and 24D are arranged at 180 ° intervals, and the two are combined to form a U-shaped communication passage (fourth communication passage 34) having a relatively large volume. The angular interval between the straight through passage portions 24A and 24B and the passage portions with lateral holes 24C and 24D is 60 °.

  Therefore, when the main valve body 20 is in the first rotation position, the straight through passage portions 24A and 24B are located right above the third port 13 and the fourth port 14, and the main valve body 20 is in the first rotation position. When rotated clockwise by 60 ° from the bottom, the lower surface openings of the straight through passage portions 24A, 24B are closed by the lower valve seat 10B, and the lower surface openings of the passage portions 24C, 24D with lateral holes are formed at the third port 13, the fourth port. Located directly above port 14.

  Since the communication passage (third communication passage 33) is formed by combining the two members of the first layer member 21 and the second layer member 22, a lateral hole is formed between the passage portions 21C and 21D with lateral holes when viewed in cross section. The guide portion bulging toward the 21E side is provided relatively long in the direction perpendicular to the center line O. The guide portion can prevent the vortex flow generated in the portion where the fluid (refrigerant) bends in a U shape, and the diameter of the lateral hole 21E and the diameter of each of the ports 11 to 14 have substantially the same passage diameter. Since the volume of the flow passage can be made uniform, the fluid does not expand or contract in the main valve 5, and the pressure loss can be reduced. If the main valve upper half 20A is made of a molded product without using a 3D printer, which will be described later, the communication passage must be a bowl type without a guide portion, and vortex flow may occur. Since the volume of the flow path cannot be made uniform, the pressure loss increases.

  At both ends of each of the communication passages 31, 32, 33, 34 described above, the valve seat surfaces 17 of the upper valve seat 10A and the lower valve seat 10B are clearly understood by referring to FIGS. 4, 5 and 7. Projections 36 having annular sealing surfaces 37, 37 that are in close contact with each other around the openings of the ports 11 to 14 in The adjacent convex portions 36, 36 (the sealing surfaces 37, 37 of the convex portions 36, 36) are connected to each other to have a spectacle shape in a plan view, and the convex portion 36 (the sealing surface 37 of the convex portion 36) provided on the fourth layer member 24. Is also the same.

  Further, as shown in FIG. 4, the first communication passage 31 and the second communication passage 32 are divided communication passages extending over the upper half portion 20A and the lower half portion 20B of the main valve body 20. The following measures have been taken to secure the sealing property. That is, to describe the first communication passage 31 as a representative, the large diameter portion 22c is formed below the linear through passage portion 22A of the second layer member 22 forming the first communication passage 31, and the third layer is formed. A cylindrical portion 23c slidably inserted into 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. And a washer 49a that prevents the O-ring 49 from falling off is joined to the end of the large diameter portion 22c by welding. The second communication passage 32 has the same structure.

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

  The ball-type seal surface separating mechanism 45 is provided between the first layer member 21 and the upper valve seat 10A, as shown in a representative example in FIGS. The housing portion 47 that houses 46 in a state of partially protruding in the up-down direction in a rotatable manner and in a state in which movement is substantially blocked, and before and after the rotation of the main valve body 20 starts and when the rotation ends. When the main valve body 20 rotates, a part of the ball 47 protruding from the accommodating portion 47 is fitted so that the seal surface 37 on the main valve body 20 side does not separate from the valve seat surface 17 of the upper valve seat 10A. When the flow path is being switched, the ball 46 is provided with an inverted conical recessed hole 48 having a size and shape that allows the ball 46 to roll down while pushing down the main valve body 20. The accommodating portion 47 is composed of a round hole 47a and a tubular retaining member 47b that is fixed to the round hole 47 by press fitting or the like and has a narrowed upper portion.

  The accommodating portion 47 accommodating the balls 46 has 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 FIG. 7 and FIG. The holes 48 are provided at four positions at 90 ° intervals, and the recessed holes 48 are the same as the accommodating portion 47 in a plan view on the same circumference of the upper valve seat 10A and the lower valve seat 10B. It is provided at a total of eight positions, that is, the position and a position 60 ° clockwise away from the position.

  In such a seal surface separating mechanism 45, before the start of rotation of the main valve body 20 and at the end of rotation, as shown in FIG. 5 (A), a part of the ball 46 is inside the recessed hole 48 of the upper valve seat 10A. It is embedded. This fitting amount (the height from the valve seat surface 17 of the upper valve seat 10A to the top of the ball 46) is h. When the main valve body 20 starts to rotate by 60 ° from this state, the accommodating portion 47 moves (rotates) in the circumferential direction, and accordingly, the ball 46 moves the main valve body 20 as shown in FIG. 5B. 20 (upper half portion 20A) rolls out from the recessed hole 48 while pushing down against the biasing force of the compression coil spring 29 that is compressed between the upper half portion 20A and the lower half portion 20B. As a result, the seal surface 37 of the main valve body 20 separates 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 amount of fitting h.

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

  As can be understood from the above description, when the main valve body 20 takes the first rotational position, the first communication passage 31 that allows the first port 11 and the third port 13 to communicate with each other is the straight through passage portion 21A, The second communication passage 32, which is a linear passage composed of 22A, 23A, and 24A, and which communicates the second port 12 and the fourth port 14, is a linear through passage portion 21B, 22B, 23B, and 24B. It will be a straight path constructed.

  On the other hand, when the main valve body 20 takes the second rotational position, the third communication passage 33 for communicating the first port 11 and the second port 12 is provided in the upper half portion 20A of the main valve body 20. A fourth communication passage 34, which is a U-shaped passage constituted by the passage portions 21C and 21D with lateral holes and which connects the third port 13 and the fourth port 14, is provided in the lower half portion 20B of the main valve body 20. A U-shaped passage is formed by the passage portions 24C and 24D with the lateral holes.

  As described above, in the flow path switching valve 1 according to the present embodiment, the main valve body 20 is rotated clockwise by 60 ° from the first rotation position, so that the ports 11-13 communicate with each other through the first communication passage 31. And between the ports 12-14 communicating with the second communication passage 32, the ports 11-12 communicating with the third communication passage 33, and the ports 13-14 communicating with the fourth communication passage. By rotating the main valve body 20 counterclockwise by 60 ° from the second rotation position, the ports 11-12 communicating with each other through the third communication passage 33 and the ports 13-14 communicating with each other through the fourth communication passage are communicated. Then, the flow path is switched between the ports 11-13 communicating with the first communication passage 31 and the ports 12-14 communicating with the second communication passage 32.

  When the flow path switching valve 1 of the present embodiment is incorporated in the heat pump type cooling and heating system as shown in FIG. 24, as described above, for example, the first port 11 is the discharge side connected to the compressor discharge side. The high-pressure port D, the second port 12 are 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. Is a low pressure port S on the suction side.

  When performing the cooling operation, the main valve body 20 is set to the first rotational position as shown in FIG. 6 (A). As a result, as shown by the white arrow in (2) of FIG. 6 (A), the high-pressure refrigerant from the compressor discharges the high-pressure port 11 (D) → the linear first communication passage 31 → outdoor entrance / exit. While flowing to the port 13 (C), the low pressure refrigerant from the indoor heat exchanger flows to the indoor inlet / outlet port 12 (E) → the second linear communication passage 32 → the suction side low pressure port 14 (S).

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

  In the flow path switching valve 1 of the present embodiment having such a configuration, the first communication passage 31 and the second communication passage 32 have a thickness (passage diameter) from the starting end to the ending end that is the first port 11 and the second port. Since the passage is a straight passage having substantially the same diameter as the port 12, and the refrigerant flows straight downward from the first port 11 and the second port 12, almost no pressure loss occurs in the main valve 5 (main valve body 20). Absent. Further, since the third communication passage 33 and the fourth communication passage 34, which are composed of the two passage portions 21C and 21D, 24C and 24D with lateral holes, have a relatively large inner volume, the pressure loss is reduced and the total amount is reduced. Therefore, the pressure loss can be considerably reduced as compared with the conventional flow path switching valve.

  Further, the main valve body 20 has a two-part configuration of an upper half portion 20A and a lower half portion 20B, and the upper half portion 20A and the lower half portion 20B can be moved up and down independently of each other, and at the same time, the upper half portion can be moved. Since the compression coil spring 29 is compressed between the lower half portion 20A and the lower half portion 20B, the spring force pushes up the upper half portion 20A and the sealing surface 37 of the compression coil spring 29 on the valve seat surface 17 of the upper valve seat 10A. While being pressed around each port 11, 12, the lower half 20B is pressed down so that its sealing surface 37 is pressed around each port 13, 14 on the valve seat surface 17 of the lower valve seat 10B.

  In this case, since the convex portion 36 is projectingly provided on the main valve body 20 (upper half portion 20A and lower half portion 20B) side and the end surface thereof is the annular seal surface 37, the portion that contacts the valve seat surface 17 Area is minimized, which increases the contact pressure. As a result, sufficient sealing performance can be secured, and valve leakage of fluid (refrigerant) leaking 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 formed in a flat plate shape, the valve seat surface 17 can be a flat smooth surface (the surface accuracy can be easily increased). The sealability can be remarkably improved as compared with the case where the surface to be sealed includes the cylindrical surface as described above.

  Further, 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, the piping can be easily handled and the substantial occupied space including the piping can be reduced. it can.

  In addition, in the present embodiment, the ball-type seal surface separation mechanism 45 pushes down the upper half portion 20A of the main valve body 20 while the main valve body 20 is rotating (during flow path switching), and Since the half portion 20B is pushed up and the sealing 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, sliding friction is almost eliminated. As a result, stick-slip or the like is less likely to occur, wear of sliding parts can be significantly suppressed, and further wear is suppressed, so sealing performance is improved and valve leakage is effectively suppressed. be able to.

  Further, in the conventional four-way switching valve having the slide type main valve body as disclosed in Patent Document 1, the flow passage opening area of the high pressure pipe D and the low pressure pipe S rapidly changes at the time of switching the flow passage, Abnormal noise (switching noise) is generated due to the fact that the high-pressure refrigerant flows into the low-pressure pipe. In order to prevent this abnormal noise, the frequency of the compressor is gradually reduced on the cooling / heating system side so that the abnormal noise due to the pressure difference between the high-pressure pipe D and the low-pressure pipe S becomes an allowable differential pressure. Therefore, it was necessary to switch the flow path. In the flow path switching valve 1 of the present embodiment, since the main valve body is floated from the valve seat surface by the amount of the fitting amount h by the ball type seal surface isolation mechanism 45, the flow path switching valve 1 is switched, so that a constant flow path opening area is provided immediately after the switching. Therefore, the flow path opening area between the high-pressure pipe D and the low-pressure pipe S does not change abruptly, and therefore the above-described abnormal noise can be suppressed. Further, by appropriately changing the amount of fitting h, the degree of decrease in the frequency of the compressor at the time of switching the flow path can be made smaller than that of the cooling / heating system using the four-way switching valve of Patent Document 1, and the frequency of the compressor can be reduced. It is also possible to switch the flow paths without decreasing the flow rate.

  Further, in the flow path switching valve 1 of the present embodiment, since the main valve body 20 (the upper half portion 20A and the lower half portion 20B) that receives high pressure has a cylindrical shape and the communication passages 31 to 34 are provided therein, Deformation (deflection) or the like as in the conventional example is unlikely to occur, and sufficient strength and durability can be secured.

  In addition to the above, when the flow path switching valve 1 of the present embodiment is used in an environment in which a high-temperature high-pressure refrigerant and a low-temperature low-pressure refrigerant flow, such as a heat pump type heating and cooling system, the communication passages 31 to 34 have main valve bodies 20. Since they are provided relatively far apart inside the main valve, the high temperature and high pressure refrigerant and the low temperature and low pressure refrigerant flow closer to each other (a thin wall separates them) than the conventional type. The amount of heat exchange in the housing can be significantly reduced, and thus the efficiency of the system can be improved.

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

  FIG. 11 shows an example in which the upper half portion 20A and the lower half portion 20B of the main valve body 20 of the first embodiment are integrated. That is, in the first embodiment, the upper half portion 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. Although the lower half portion 20B is composed of 24 and 24, in this example, the upper half portion 20A and the lower half portion 20B are integrally manufactured from the beginning with a 3D printer or the like. The other structure is the same as that of the first embodiment, and substantially the same operational effect as that of the first embodiment can be obtained.

  FIG. 12 shows an example in which the upper half portion 20A and the lower half portion 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 integrated body from the beginning by a 3D printer or the like. In this example, it is not possible to provide a means for urging 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 path switching valve 2 of the second embodiment is different from the first embodiment only in the structure of the communication passage provided in the main valve body 20 of the first embodiment, and the other structures are substantially the same. Illustration of parts common to the flow path switching valve 1 is simplified or omitted, and in the following, only different points (communicating passage configuration) will be mainly described. 13 to 15, parts corresponding to the parts of the flow path switching valve 1 of the first embodiment are designated by common reference numerals.

  13A shows a state in which the main valve body 20 is in the first rotation position, and FIG. 13B shows a state in which the main valve body 20 is rotated 90 degrees clockwise from the first rotation position in the second rotation position. FIG. 3 shows a state of being in a position, (1) is an upper surface side layout drawing, (2) is a schematic view showing a communication passage configuration in each state, and (3) is a lower surface side layout drawing.

  FIG. 14A shows (1) the first layer member 21, (2) the second layer member 22, and (3) the main valve body 20 in the second embodiment in the first rotation position. Each of the plan views of the three-layer member 23 and (4) fourth layer member 24, (B) shows the communication passage configuration in the state where the main valve body 20 is at the first rotation position, and (1) of (B). )-(4) is sectional drawing which follows the 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, () when the main valve body 20 is in the second rotation position. 4) Each of the plan views of the fourth layer member 24, (B) shows the communication passage configuration in the state where the main valve body 20 is in the second rotation position, and the upper stage side and the lower stage of (1) of (B). The side is a partial cross-sectional view taken along the line U-U and line V-V in (1) of (A), respectively, (2) and (3) of (B) are (2) and () of (A). 3) is a cross-sectional view taken along the line YY, and (B) is a partial cross section taken along the line J-J and line K-K in (4) of (A). It is a figure.

  When the flow path switching valve 2 of this embodiment is incorporated in a heat pump type cooling and heating system as shown in FIG. 24, unlike the first embodiment, for example, the first port 11 is connected to the compressor discharge side. The discharge side high pressure port D, the second port 12 is the suction side low pressure port S connected to the compressor suction side, 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 indoor side inlet / outlet port E is connected to the indoor heat exchanger.

  Then, in the main valve body 20 of the flow path switching valve 2 of the second embodiment, the first communication passage 41 and the first communication passage 41 that allow the first port 11 and the third port 13 to communicate with each other when taking the first rotational position. A second communication passage 42 that connects the fourth port 14 and the second port 12 is provided, and when the second rotation position is obtained by rotating the first rotation position by 90 ° clockwise, A third communication passage 43 that communicates with the fourth port 14 and a fourth communication passage 44 that communicates with the third port 13 and the second port 12 are provided.

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

  In the first layer member 21 forming the upper part of the main valve body upper half portion 20A, two linear through passage portions 41A are provided at 180 ° intervals, similarly to the linear through passage portions 21A and 21B of the first embodiment. 41B is provided. In addition, as shown in the upper side and the lower side of (1) of FIG. 15 (B), the passage portions 41C and 41D with lateral holes having one end opened (upper surface openings 41a and 41c) and the entire lower surface side are opened. It is provided. The upper surface openings 41a, 41c of the passage portions 41C, 41D with the lateral holes are arranged at positions separated by 90 ° from the straight through passage portions 41A, 41B, and the lower surface openings other than the other end portion are closed by the second layer member 22. The other ends (lower surface openings 41b and 41d) that are not closed by the second layer member 22 are arranged 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 rotation 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 rotation position. When rotated 90 ° clockwise, the upper surface openings of the straight through passage portions 41A, 41B are closed by the upper valve seat 10A, and the upper surface openings of the passage portions 41D, 41C with lateral holes are formed in the first port 11 and the second port 12. Located just below.

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

  The third layer member 23, which constitutes the upper part of the main valve body lower half portion 20B, includes four straight line passages directly below the four straight line passage portions 42A, 42B, 42C, 42D provided in the second layer member 22. Road portions 43A, 43B, 43C, 43D are provided.

  The fourth layer member 24, which constitutes the lower part of the lower half portion 20B of the main valve body, has two linear through passage portions 44A at 180 ° intervals, like the linear through passage portions 21A and 21B of the first embodiment. 44B is provided. Further, as shown in the upper side and the lower side of (4) of FIG. 15 (B), the passage portions 44C, 44D with lateral holes having one end open (lower surface openings 44a, 44c) and the entire upper surface side are opened. It is provided. The lower surface openings 44a and 44c of the lateral holed passage portions 44C and 44D are arranged at positions separated by 90 ° from the straight through passage portions 41A and 41B, and the upper surface openings other than the other end portion are closed by the third layer member 23. The other ends (upper surface openings 44b and 44d) that are not closed by the third layer member 23 are arranged on a straight line connecting the centers of the straight through passage portions 44A and 44B.

  Therefore, when the main valve body 20 is at the first rotation position, the straight through passage portions 44A and 44B are located directly above the third port 13 and the fourth port 14, and the main valve body 20 is at the first rotation position. When rotated 90 degrees clockwise from, the lower surface openings of the straight through passage portions 44A, 44B are closed by the lower valve seat 10B, and the lower surface openings 44c, 44a of the passage portions 44D, 44C with lateral holes are formed in the third port 13. , Directly above the fourth port 14.

  As can be understood from the above description, when the main valve body 20 takes the first rotational position, the first communication passage 41 that allows the first port 11 and the third port 13 to communicate with each other is the straight through passage portion 41A, The second communication passage 42, which is a linear passage composed of 42A, 43A, and 44A, and which communicates the fourth port 14 and the second port 12, is a straight through passage portion 41B, 42D, 43D, and 44B. It will be a straight path constructed.

  On the other hand, when the main valve body 20 takes the second rotational position, the third communication passage 43 that communicates the first port 11 and the fourth port 14 has a passage portion 41D with a lateral hole in order from the top → a straight through passage portion. The crank-shaped passage is constituted by 42C → straight through passage portion 43C → transverse hole passage portion 44C. In addition, the fourth communication passage 44 that communicates the third port 13 and the second port 12 is composed of a passage portion 44D with a horizontal hole, a straight through passage portion 43B, a straight through passage portion 42B, and a passage portion 41C with a horizontal hole in order from the bottom. It becomes a crank-shaped passage.

  As described above, in the flow path switching valve 2 of the present embodiment, by rotating the main valve body 20 clockwise by 90 ° from the first rotation position, the ports 11-13 communicating with each other through the first communication passage 41 are communicated. And between the ports 14-12 communicating with the second communication passage 42, between the ports 11-14 communicating with the third communication passage 43, and between the ports 13-12 communicating with the fourth communication passage 43. By rotating the main valve body 20 counterclockwise by 90 ° from the second rotation position, between the ports 11-14 communicating with the third communication passage 43 and between the ports 13-12 communicating with the fourth communication passage. Then, the flow paths are switched between the ports 11-13 communicating with the first communication passage 41 and the ports 14-12 communicating with the second communication passage 42.

  When the flow path switching valve 2 of the present embodiment is incorporated in a heat pump type cooling and heating system as shown in FIG. 24 and the cooling operation is performed, the main valve body 20 is shown as (1) in FIG. 13 (A). The first rotational position as shown in FIG. As a result, as shown by the white arrow in (2) of FIG. 13 (A), the high-pressure refrigerant from the compressor discharges the high-pressure port 11 (D) → the linear first communication passage 41 → outdoor entrance / exit. While flowing to the port 13 (C), the low-pressure refrigerant from the indoor heat exchanger flows to the indoor-side inlet / outlet port 14 (E) → the second linear communication passage 42 → the suction-side low-pressure port 12 (S).

  On the other hand, when performing the heating operation, the main valve body 20 is rotated 90 ° clockwise from the first rotation position to obtain the second rotation position as shown in (1) of FIG. 13 (B). Let As a result, the flow paths are switched, and as shown by the white arrow in (2) of FIG. 13B, the high pressure refrigerant from the compressor is discharged from the high pressure port 11 (D) to the crank-shaped first port. The low pressure refrigerant from the outdoor heat exchanger flows from the three communication passages 43 to the indoor inlet / outlet port 14 (E), and the low pressure refrigerant from the outdoor heat exchanger 13 (C) to the crank-shaped fourth communication passage 44 to the suction low pressure port. It flows to 12 (S).

  Also in the flow path switching valve 2 of the present embodiment having such a configuration, substantially the same operational effect as in the first embodiment can be obtained.

[Third Embodiment of Main Valve]
FIG. 16 shows the flow path switching valve of the third embodiment, (A) in a state where the main valve body is in the first rotation position, and (B) in a state where the main valve body is in the second rotation position. Yes, (1) is a top surface side layout diagram, and (2) is a cross-sectional view taken along the line X-X of (1). Note that, in FIG. 16, parts corresponding to the respective parts of the flow path switching valve 1 of the first embodiment are designated by common reference numerals.

  The flow path switching valve 3 of the third embodiment is a three-way switching valve, does not have the second port 12 provided in the main valve housing 10 of the first embodiment, and has the first layer member 21 and the second layer. It is integrated with the member 22 (since 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, 24B and the passage portions 21C, 21D with lateral holes and the portions associated therewith are deleted.

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

  Also in the flow path switching valve 3 of the present embodiment having such a configuration, there is a difference between the three-way switching valve and the four-way switching valve, but substantially the same operational effect as the four-way switching valve 1 of the first embodiment is obtained. To be

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

[Example 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.

  The actuator 7 of the first embodiment is a fluid pressure type that utilizes a differential pressure between a high pressure fluid and a low pressure fluid flowing in the main valve 5, and is provided 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 by fixing a cylindrical body 51 extending downward from the lower valve seat 10B and a lower surface opening of the body 51 in an airtight manner. , A bottom wall closing member 52 having a convex portion 52a in the center, and a thick disc-shaped seal which is fixed by caulking so as to seal the upper surface opening of the body portion 51 and further fixed by soldering, brazing, welding or the like. The upper wall closing member 53 also serving as a member and a stopper is provided with a working chamber 55 therein, and the working chamber 55 has a thick bottomed cylindrical pressure receiving moving body 60 that constitutes a motion converting mechanism 58. The pressure receiving moving body 60 accommodates a rotation driving body 65 in the form of a short cylinder that is inserted relatively rotatably as the pressure receiving moving body 60 moves in the vertical direction. Since the rotation driving body 65 is rotatably supported by the main body 50, the rotation driving body 65 does not move in the up and down direction in the working chamber 55, but is relatively moved as the pressure receiving moving body 60 moves in the up and down direction. In addition, the pressure receiving moving body 60 is rotated (described in detail later).

  A packing near the lower end of the outer periphery of the pressure-receiving movable body 60 is hermetically sealed between the inner peripheral surface of the working chamber 55 and the working chamber 55 into a variable volume upper portion 55A and a lower portion 55B. 62 is attached, and at the upper part of the outer periphery of the pressure-receiving movable body 60, operation pins 63 are respectively fitted in the key grooves 54 extending in the height direction, which are provided at two places on the left and right in the upper half of the inner periphery of the body 51. It is fixed by press fitting.

  Due to the operation pin 63 and the key groove 54, the pressure receiving moving body 60 moves linearly up and down, but its rotation is prevented.

  Note that FIG. 17 shows a state in which the pressure receiving moving body 60 is at the lowermost position (down movement stroke completion state), and FIG. 18A shows a state in which the pressure receiving moving body 60 is at the highest rising position (upper position). The movement stroke completed state) is shown (detailed later).

  In addition, an upper port 56 for introducing and discharging high-pressure fluid to the upper working chamber 55A is provided in the upper portion of the main body 50, and a high-pressure fluid is provided in the lower working chamber 55B at the bottom (lower surface closing member 52). There is provided a lower port 57 for introducing and discharging.

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

  In detail, the pressure receiving moving body 60 is provided with a plurality of (two in this embodiment) balls 72 and a housing portion 74 thereof, and the rotation driving body 65 is vertically bent around the outer periphery thereof while bending in the circumferential direction. A plurality of (two in this embodiment) spiral grooves 75 extending in the direction are provided. The accommodating portion 74 includes a ball 72 in a state where a part of the ball 72 is projected inward in the radial direction 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. The spiral groove 75 is rotatably accommodated in a state in which the movement is substantially prevented, and the spiral groove 75 is rotated by inserting a part of the ball 72 protruding inward in the radial direction from the accommodating portion 74. It consists of a shallow groove with an arcuate cross-section that allows free contact.

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

  The downward step surface of the step formed by the first expanded diameter portion 76ab and the second expanded diameter portion 76ac and the upper surface of the upper surface closing member 53 come into contact with each other, whereby the rotary drive shaft portion 76 and the rotary drive fixed thereto. The body 65 is prevented from slipping out, and the downward step surface of the step formed by the insertion portion 76aa and the first expanded diameter portion 76ab is used when the rotary drive body 65 is caulked and fixed to the rotary drive shaft portion 76. It is considered to be the receiving surface.

  Here, the rotation axis Q (rotational drive shaft portion 76) of the rotation drive body 65 is eccentric with respect to the rotation axis O of the main valve body 20, and is arranged parallel to the rotation axis O of the main valve body 20. A rotation transmission mechanism 77 that transmits the rotation of the rotary drive body 65 to the main valve body 20 is provided between the rotary drive shaft portion 76 and the lower rotary shaft portion 30B of the main valve body 20.

  The rotation transmission mechanism 77 has its base end portion coupled and fixed to the intermediate portion 76b of the rotation drive shaft portion 76, and its distal end center, as can be seen by referring to FIG. 19 in addition to FIGS. 17 and 18 (A). A drive arm 78 in which a U-shaped engaging groove 78a is formed, and a base end portion thereof are connected and fixed to a pivot shaft portion 30c of the lower rotary shaft portion 30B of the main valve body 20, and the U-shaped portion is provided near the tip thereof. An engaging pin 79 that slidably engages with the engaging groove 78a is formed of a driven arm 39 that extends vertically.

  In the rotation transmission mechanism 77 having such a configuration, when the rotation drive shaft portion 76 rotates, the drive arm 78 rotates (swings) integrally with the rotation drive shaft portion 76, and along with this, the vicinity of the tip of the driven arm 39 (the engagement pin 79) is driven. The arm 78 is rotated around the tip (U-shaped engaging groove 78a) of the arm 78, whereby the lower rotary shaft portion 30B and the main valve body 20 rotate. In this case, in the present embodiment, the rotation angle θ of the driven arm 39 is set to 60 °, which is the rotation angle required by the main valve body 20 for switching 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 (leverage ratio) of the drive arm 78 and the driven arm 39, and the like. It should be noted that FIGS. 17, 18A, and 21A to 21D described later show the intermediate states of rotation of the drive arm 78 and the driven arm 39.

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

  Next, the operation inside 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).

  17 and 21 (A) show a state in which a high-pressure fluid (high-pressure refrigerant) is introduced into the upper working chamber 55A through the upper port 56 and the high-pressure fluid is discharged from the lower working chamber 55B through the lower port 57. Shows. When the high-pressure fluid is introduced into the working chamber upper portion 55A, the high-pressure fluid extends to every corner of the space (upper working chamber upper portion 55A) above the packing 62 mounted on the pressure receiving moving body 60 and below the upper surface closing member 53, that is, A portion between the bottom surface of the pressure receiving moving body 60 and the lower surface of the rotary driving body 65 and the main body portion 50 via a gap formed between the inner peripheral surface of the pressure receiving moving body 60 and the outer peripheral surface of the rotary driving body 65. Since the gap is formed between the inner peripheral surface of the body portion 51 and the outer peripheral surface of the pressure receiving movable body 60, the pressure receiving area on the upper surface side of the pressure receiving movable body 60 is equal to the pressure receiving area on the lower surface side.

  With such a configuration, in the state shown in FIGS. 17 and 21 (A), high-pressure fluid is introduced into the lower working chamber 55B through the lower port 57, and the upper port 56 is moved from the upper working chamber 55A. When the high-pressure fluid is discharged through the working chamber 55A, the working chamber lower portion 55B has a higher pressure than the working chamber upper portion 55A, so that 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 straight up, and along with this, the ball 72 of the motion conversion mechanism 58 also moves straight up while rotating. At this time, the spiral groove 75 is pushed in the circumferential direction by the portion of the ball 72 fitted in the spiral groove 75, and the rotary drive body 65 rotates in one direction (here, clockwise). Then, when the upper end (annular pressing member 66) of the pressure receiving moving body 60 contacts the upper surface closing member 53, the upward movement of the pressure receiving moving body 60 stops and the rotation of the rotary drive body 65 also stops. Hereinafter, this stroke is referred to as an upward stroke, and the state shown in FIG. 21B (the state in which the pressure receiving moving body 60 is at the highest position) is referred to as the upward stroke completed state.

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

  By causing the pressure receiving moving body 60 to take the downward stroke in the state where the upward stroke is completed, the main valve body 20 rotates from the first rotation position to the second rotation position, and the flow path switching as described above is performed. On the contrary, by causing the pressure receiving moving body 60 to take an upward stroke in the state where the downward stroke is completed, the main valve body 20 rotates from the second rotation position to the first rotation position. The flow path switching is performed as described above.

  In the present embodiment, the switching of the flow paths, that is, the switching between the upper stroke and the lower stroke is performed by the upper port 56 and the lower port 57, and the high pressure portion in the main valve housing 10 and the low pressure portion. The electromagnetic four-way pilot valve 80 is connected to the four ports 14 (suction side low pressure port S).

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

  The inside of the valve case portion 81 is a valve chamber 88, and this valve chamber 88 communicates with the inside of the main valve housing 10, which is a high-pressure portion, through a pore 89 penetrating the lower valve seat 10B. It has become. The solenoid portion 82 includes a coil 82a for energizing and energizing, a cover case 82b for covering the outer circumference of the coil 82a, a suction element 84 arranged on the inner circumference side of the coil 82a and fixed to the cover case 82b by a bolt 82c, and a suction element 84 for this suction. A plunger 85 and the like arranged to face the child 84 are provided. The plunger 85 is slidably fitted into a cylindrical guide pipe 86 whose lower portion is arranged between the coil 82a 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.

  Further, a compression coil spring 87 that urges the plunger 85 in a direction away from the suction element 84 (upward in the drawing) is provided between the suction element 84 and the plunger 85.

  A valve body holder 90, which holds the valve body 91 slidably in the thickness direction at its free end side, is press-fitted at its proximal end together with the fitting 96 at the end of the plunger 85 opposite to the suction element 84 side. -Mounted and fixed by caulking. A leaf spring 94 is attached to the valve body holder 90 to urge the valve body 91 in a direction (thickness direction) to press the valve body 91 against 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 this order from the top, and the valve body 91 selectively communicates the port a with the port b and the port b with the port c. A concave portion 93 that is recessed in the thickness direction is provided. In the valve seat block 83, one end of the thin tube 95a is connected to only the port a, one end of the thin tube 95b is connected to only the port b, and one end of the thin tube 95c is connected to only the port c. Are airtightly inserted.

  The other end of the thin tube 95a is connected to the working chamber upper portion 55A via 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 (suction side low pressure port S) which is a low pressure portion. The other end of the thin tube 95c is connected to the lower working chamber 55B via the lower port 57 of the main body 50.

  In the four-way pilot valve 80 having such a configuration, when the energization of the solenoid portion 82 is OFF, the plunger 85 has its upper end valved by the urging force of the compression coil spring 87 as shown in FIG. It is pushed up to the position where it abuts on 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 thereof allows the port a and the port b to communicate with each other and the port c and the valve chamber 88 to communicate with each other. The high-pressure fluid is introduced into the lower working chamber 55B through the pores 89 → the valve chamber 88 → the port c → the narrow tube 95c → the lower port 57, and the high-pressure fluid in the upper working chamber 55A is the upper port 56 → the narrow tube 95a → the port a. -> Concave portion 93-> Port b-> Small tube 95b-> Fourth port 14 (suction side low-pressure port S) and is discharged.

  On the other hand, when the energization of the solenoid portion 82 is turned on, the plunger 85 is attracted by the suction force of the suction element 84 to the position where the lower end of the plunger 85 contacts the suction element 84, as shown in FIG. . At this time, the valve element 91 is located on the port b and the port c, and the recess 93 thereof allows the port b and the port c to communicate with each other and the port a and the valve chamber 88 to communicate with each other, so that the high pressure in the main valve housing 10 is high. The fluid is introduced into the upper working chamber 55A through the pores 89 → the valve chamber 88 → the port a → the narrow tube 95a → the upper port 56, and the high pressure fluid in the lower working chamber 55B is the lower port 57 → the narrow tube 95c → the port c → The recess 93 flows to the port b, the narrow tube 95b, 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 upward stroke is taken, the main valve body 20 rotates from the second rotation position to the first rotation position, and the flow passage switching as described above is performed. On the other hand, when the energization of the solenoid portion 82 is turned on, the downward stroke is taken, the main valve body 20 rotates from the first rotation position to the second rotation position, and the flow path as described above is obtained. Switching is performed.

  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 in the main valve 10 is switched by switching ON / OFF the energization of the electromagnetic four-way pilot valve 80. Since the main valve body 20 is rotated by utilizing, the cost reduction, the power consumption reduction, the energy saving, etc. can be achieved as compared with the case where the main valve body 20 is rotated by an electric motor or the like. You can The flow passage switching by the actuator 7 of this embodiment can be performed more quickly than the flow passage switching performed by the electric motor + the speed reducer.

  Further, the actuator 7 for rotating the main valve body 20 is configured to vertically move the pressure receiving moving body 60 by fluid pressure, convert the vertical movement into a rotary motion and transmit the rotary motion to the main valve body 20. The part that receives high pressure as compared to a plate-shaped body that has a large pressure receiving area with respect to the plate thickness, where the part that receives high pressure is cantilevered by the extension shaft of the rotary shaft of the main valve body. Sufficient strength can be ensured in the (pressure-receiving moving body 60), durability can be improved, and sufficient strength can be ensured, so that the pressure-receiving area can be increased, 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 a linear motion into a rotary motion.However, since a normal ball screw mechanism uses many balls and requires a return structure, Compared with the motion conversion mechanism 58 of the example, the structure is complicated and expensive, and since it is not considered to be used in a high temperature and high pressure environment, it should be used for a flow path switching valve incorporated in a heat pump type cooling and heating system or the like. Is difficult On the other hand, the fluid pressure type actuator including the motion converting mechanism 58 of the present embodiment has an extremely simple configuration with a small number of parts, and is therefore advantageous in terms of cost and a measure when used in a high temperature and high pressure environment. (The wall thickness of the pressure receiving moving body 60 is made thicker) can be easily taken. Therefore, the flow path switching valve 1 of the present embodiment is particularly suitable for a flow assembled 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 directional control valve.

[Modification of actuator]
FIG. 23 shows a modification of the actuator. The actuator 8 of the illustrated example has a basic configuration similar to that of the actuator 7 described above, including a main body portion 50, a motion converting mechanism 58 (pressure receiving moving body 60, rotation driving body 65, ball 72, accommodating portion 74, spiral groove 75), upper port. 56, the lower port 57, the four-way pilot valve 80, etc. (reference numerals are common), but in the actuator 8 of this example, the drive shaft portion of the rotary drive body 65 and the rotary shaft portion of the main valve body 20 are common. The main valve body 20 and the rotary drive body 65 are arranged on the axis so as to rotate integrally.

  Specifically, the rotary drive body 65 is externally fitted and fixed to the lower rotary shaft portion 30B of the main valve body 20 by press fitting, caulking, etc., so that 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 10e of the lower valve seat 10B. The upper surface closing member 53 is also unnecessary. Therefore, the configuration is simplified and it is advantageous in terms of cost.

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

  Further, as the material of the valve housing 10, the main valve body 20, the pressure receiving moving body 60, the rotary drive body 65 and the like, aluminum, stainless steel or the like is used, but the material is not limited thereto, and other metals, resins, etc. Any material may be used as long as it can withstand the pressure of the introduced fluid.

1 flow path switching valve 5 main valve 7 actuator 10 main valve housing 10A upper valve seat 10B lower valve seat 11 first port 12 second port 13 third port 14 fourth port 17 seat surface 20 main valve body 20A upper half 20B Lower half 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 rotation shaft portion 30B Lower rotation shaft portion 31 First communication passage 32 Second Communication passage 33 Third communication passage 34 Fourth communication passage 36 Convex portion 37 Sealing surface 41 First communication passage 42 Second communication passage 43 Third communication passage 44 Fourth communication passage 45 Ball type seal surface separating mechanism 50 Main body (actuator )
52 Lower surface closing member 53 Upper surface closing member 54 Key groove 55 Working chamber 55A Working chamber upper part 55B Working chamber lower part 56 Upper port 57 Lower port 58 Motion conversion mechanism 60 Pressure receiving moving body 62 Packing 63 Working pin 65 Rotation driving body 72 Ball 75 Spiral groove 76 Rotational 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 Recess a, b, c Port (four-way pilot valve )
95a, 95b, 95c Capillary tube D High-pressure port on discharge side S Low-pressure port on suction side C Outdoor entrance / exit port E Indoor entrance / exit port

Claims (9)

At least three in total are provided in the tubular main valve housing, the upper and lower openings of which are hermetically sealed by the upper valve seat and the lower valve seat, and the upper valve seat and / or the lower valve seat. A main valve having a main valve body rotatably disposed in the main valve housing, and an actuator for rotating the main valve body,
A plurality of communication passages for selectively communicating between the ports are provided in the main valve body, and by rotating the main valve body, the communicating ports are switched.
The main valve body has a two-part configuration of an upper half part and a lower half part that are integrally rotatable and can move up and down.
The lower half and the upper half is to have a U-shaped communication passage, respectively,
Between the upper half and the lower half, biasing means for biasing them in mutually opposite directions are interposed.
As one of the communication passages, there is a divided communication passage that extends over the upper half portion and the lower half portion, and the lower end portion of the upper half portion and the upper end portion of the lower half portion of the divided communication passage are on the other hand with the large diameter portion is formed, the cylindrical portion is extended to the the other is inserted into the large diameter portion, the Rukoto O-ring is interposed between the large diameter portion and the cylindrical portion Characteristic flow path switching valve. In the main valve body, at least one first communication passage capable of communicating at least one of the ports with another one and at least one communication passage capable of communicating with one of the ports with another one A second communication passage is provided, and by rotating the main valve element in one direction, the flow passage can be switched from between ports communicating with the first communication passage to ports communicating with the second communication passage. By switching the main valve element in the other direction after switching the flow path, the flow path is switched from the port communicating with the second communication path to the port communicating with the first communication path. The flow path switching valve according to claim 1 , wherein the flow path switching valve is configured to be opened. The upper valve seat and / or the lower valve seat is provided with first, second, third and fourth ports,
A first communication passage communicating with the first port and the third port and a communication passage communicating with the second port with the fourth port when the main valve body is in the first rotation position; 2 passages,
A third communication passage for communicating the first port with the second port or the fourth port and a communication of the third port with the fourth port or the second port when the main valve body takes the second rotational position. The flow path switching valve according to claim 1 or 2 , further comprising a fourth communication passage that allows the passage. The flow path switching valve according to claim 3 , wherein the upper valve seat is provided with first and second ports, and the lower valve seat is provided with third and fourth ports. The flow path switching valve according to any one of claims 1 to 4 , wherein at least one of the plurality of communication paths is configured by a linear path as a whole. A projection having an annular sealing surface that is in close contact with the periphery of the opening of each port in the upper valve seat and / or the lower valve seat is projected at both ends of the communication passage. The flow path switching valve according to any one of 1 to 5 . Between the upper half portion and the upper valve seat and between the lower half portion and the lower valve seat, when the main valve body rotates, the sealing surface on the main valve body side is provided with the upper valve seat and flow path switching valve according to any one of claims 1 6, characterized in that the ball-type sealing surface spaced mechanism giving away from said lower valve seat is provided. The ball-type seal surface separating mechanism includes a ball, an accommodating portion for accommodating the ball in a state in which a part of the ball is protruded in a vertical direction, and is rotatably and substantially prevented from moving, Before the start of rotation and at the end of rotation of the valve body, a part of the ball protruding from the accommodating portion so that the sealing surface on the main valve body side does not separate from the upper valve seat and the lower valve seat. And a recessed hole having a size and shape such that when the main valve body is rotated, the ball pushes down the upper half portion and rolls out while pushing up the lower half portion, The accommodating portion is provided at two or more locations on the same circumference of the upper half portion and the lower half portion, and the recessed hole is on the same circumference of the upper valve seat and the lower valve seat. At the same position as the storage section Flow path switching valve according to claim 7, characterized in that the main valve body is provided at an angle component away rotating the flow channel switching from fine said position. The actuator has a main body portion provided with a working chamber into which the high-pressure fluid supplied to the main valve is introduced, and the reciprocating linear motion is reversed in the working chamber by utilizing the pressure of the high-pressure fluid. The flow path switching valve according to any one of claims 1 to 8 , further comprising a motion conversion mechanism that converts rotational motion in both directions.

Images