JP6478780B2 - Flow path switching valve - Google Patents

Description

  The present invention relates to a rotary flow path switching valve that switches a flow path by rotating a valve body, and more particularly to a flow path switching valve that is suitable for performing flow path switching in a heat pump air conditioning system or the like.

  Generally, a heat pump type air conditioning system such as a room air conditioner or a car air conditioner has 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, and the like. It has.

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

  The 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 line arrow in FIG. The high pressure port D is connected to the outdoor side input / output port C, and the indoor side input / output port E is connected to 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 led from the compressor 110 to the outdoor heat exchanger 120 through the flow path switching valve 140, where it is condensed by exchanging heat with outdoor air. 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 heats (cools) the indoor air and evaporates, and the indoor heat exchanger 130 has a low temperature. The low-pressure refrigerant is returned to the suction side of the compressor 110 via the flow path switching valve 140.

  On the other hand, when the heating operation mode is selected, the discharge side high pressure port D of the flow path switching valve 140 is set to the indoor side input / output port E and the outdoor side input / output port C is set as shown by the broken line arrow in FIG. The high-pressure and high-pressure refrigerant is communicated to the suction-side low-pressure port S, respectively, and the high-temperature and high-pressure refrigerant is led from the compressor 110 to the indoor heat exchanger 130. Are introduced into the expansion valve 160. The expansion valve 160 decompresses the high-pressure refrigerant, and the decompressed low-pressure refrigerant is introduced into the outdoor heat exchanger 120 where it evaporates by exchanging heat with the outdoor air, and the outdoor heat exchanger 120 generates a low-temperature and low-pressure refrigerant. The refrigerant is returned to the suction side of the compressor 110 through the flow path switching valve 140.

  As a four-way switching valve incorporated in a heat pump type air conditioning system as described above, there has been conventionally known a valve body (valve housing) incorporating a slide type main valve body and an electromagnetic pilot valve ( For example, see Patent Document 1). In the flow path switching valve described in Patent Document 1, a discharge-side high-pressure port D, an outdoor-side input / output port C, a suction-side low-pressure port S, and an indoor-side input / output port E are formed in the valve housing. A sliding main valve body is slidably arranged in the left-right direction so as to create a communication state of ports D → C and E → S or ports D → E and C → S (switching the flow path). . The left and right sides of the sliding main valve body in the valve housing are introduced with a high pressure refrigerant on the compressor discharge side and a low pressure refrigerant on the suction side of the compressor via a pilot valve, respectively. The high-pressure chamber and the low-pressure chamber defined by the piston type packing are provided, and the flow path is switched by sliding the sliding main valve body in the left-right direction using the pressure difference between the high-pressure chamber and the low-pressure chamber. Have been to do.

  On the other hand, Patent Document 2 proposes a rotary type four-way switching valve provided with a pilot valve. This four-way switching valve divides the inside of the cylindrical body (main valve housing) into two parts by a partition piece (a plate-like main valve body that is cantilevered and supported by 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 opposite each other by about 180 ° to rotate the plate-shaped main valve body. By switching the flow path, that is, the first communication state in which the discharge-side high-pressure port D communicates with the outdoor-side input / output port C and the indoor-side input / output port E communicates with the suction-side low-pressure port S, and the discharge-side high-pressure port D Is created in the second communication state in which the outdoor input / output port C and the outdoor input / output port C communicate with the suction side low pressure port S, respectively. Installed on the upper side of the main valve housing A fluid pressure type actuator that utilizes the differential pressure between the high-pressure refrigerant and low-pressure refrigerant in the system (partitioned by a plate-like main valve element that is cantilevered on the extended shaft part of the rotary shaft part of the plate-like main valve element) This is done by selectively introducing and discharging the high-pressure refrigerant into the two working chambers 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 described in Patent Document 1, a high-pressure fluid (refrigerant) collides with an inner wall surface or the like in a valve housing having a relatively small internal volume, and its flow direction changes greatly. I don't like to increase the pressure loss, and the slide-type main valve body with a pair of left and right piston type packings slides to switch the flow path, so the sliding part is easily worn by stick-slip etc. As a result, there is a problem that the sealing performance of the sliding portion is deteriorated and valve leakage is likely to occur.

  Further, in the rotary flow path switching valve described in Patent Document 2, the main valve body that receives high pressure is a cantilevered plate-shaped body having a large pressure receiving area with respect to the plate thickness. (Flexure) etc. are likely to occur, there is a problem in strength and durability, and since the surface to be sealed includes a cylindrical surface, the sealing performance is likely to be impaired due to the fact that the deformation (flexure) etc. is likely to occur. There is also a problem that valve leaks easily.

  In addition, the high-pressure fluid collides with the plate-like main valve body and the inner wall surface in the main valve housing, and the flow direction thereof is greatly changed, so that the pressure loss is increased, and there are approximately 90 at four locations on the outer periphery of the main valve housing. Since the ports are provided at intervals of 0 °, the piping is troublesome, and there is a problem that the substantial occupied space including the pilot valve and the piping becomes extremely large.

  In addition to the above, in a conventional flow path switching valve, in particular, a four-way switching valve used in the heat pump type air conditioning system described above, a high-temperature high-pressure refrigerant and a low-temperature low-pressure refrigerant are in close proximity (thin wall) in the main valve housing. Therefore, there is also a problem that the heat exchange amount in the main valve housing becomes large and the efficiency of the system is deteriorated.

  Further, in the flow path switching valve described in Patent Document 2, even in the fluid pressure type actuator for rotating the main valve body (flow path switching), the portion that receives high pressure is plate-like as in the main valve body side. Since it is a plate-like body with a large pressure-receiving area relative to the plate thickness, which is cantilevered on the extension shaft of the main shaft, it is prone to deformation (bending), and there is a problem in strength and durability. is there.

  In addition, in the conventional flow path switching valve, in particular, the four-way switching valve used in the heat pump type air conditioning system described above, there is a possibility that foreign matter from the compressor may be mixed in the main valve housing. At the time of switching, there is a risk that the sliding main valve body or plate main valve body slides into each port with the foreign matter bitten, and the surface to be sealed may be damaged. The problem that it is easy to be damaged and valve leakage easily occurs.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to suppress pressure loss and wear of sliding parts as much as possible, improve sealability, and prevent valve leakage. To provide a flow path switching valve that can be difficult, can secure sufficient strength to withstand high pressure, can improve durability, and can be used for piping and reduction of occupied space. It is in.

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

  In order to achieve the above object, the flow path switching valve according to the present invention is basically a cylindrical main body whose upper and lower openings are hermetically sealed by an upper valve seat and a lower valve seat. A total of at least three ports are provided in the valve housing, the upper valve seat and / or the lower valve seat, and the main valve housing is rotatably arranged and selectively communicates between the ports. A main valve having a main valve body provided with a plurality of communication passages, and an actuator for switching between ports communicating with each other by rotating the main valve body, the main valve body and the upper side During rotation of the main valve body between the valve seat and / or between the main valve body and the lower valve seat, the seal surface on the main valve body side is the upper valve seat and / or the lower side Sealing surface separation mechanism for separating from the valve seat , A part of which is fixed to the upper end surface of the main valve body on the upper valve seat side and / or the lower end surface of the lower valve seat side, and the other part is the upper valve seat side and / or the lower valve seat. The leaf spring is biased to the side, and when the main valve body rotates, the other part of the leaf spring is pressed against the upper valve seat and / or the lower valve seat by elastic deformation of the leaf spring. A foreign matter removing means that slides around the opening of the port in the valve seat surface of the upper valve seat and / or the lower valve seat in a state to remove foreign matter present on or near the valve seat surface. It is characterized by being.

  In a preferred aspect, the leaf spring of the foreign matter removing means is fixed to a storage groove formed on the upper end surface and / or the lower end surface of the main valve body.

  In a further preferred aspect, at both ends of the communication path, convex portions having an annular seal surface that is in close contact with the opening of each port in the upper valve seat and / or the lower valve seat are projected, and The storage groove is formed so that at least a part thereof overlaps the convex portion.

  In another preferred embodiment, the leaf spring is provided along the radial direction of the main valve body, and at least of the periphery of the port opening in the valve seat surface of the upper valve seat and / or the lower valve seat. A dimension shape is set so that the said annular seal surface of the said convex part may slide to the part which closely_contact | adheres.

  In a further preferred aspect, the leaf spring has a V shape when viewed in a cross section perpendicular to the radial direction of the main valve body, and the top thereof is fixed to the upper end surface and / or the lower end surface of the main valve body, The both leg portions are biased toward the upper valve seat side and / or the lower valve seat side.

  In another preferred aspect, the leaf spring is disposed between the communication passages communicating with the port before the rotation of the main valve body and at the end of the rotation.

  In a further preferred aspect, the leaf spring is also disposed on the opposite side of the communication passage from the communication passage communicating with the port before the rotation of the main valve body and at the end of the rotation. The

  In this case, in a preferred embodiment, the main valve body has a two-part configuration of an upper half part and a lower half part that are integrally rotatable and vertically movable, and between the upper half part and the lower half part. , And biasing means for biasing them in opposite directions are interposed between the upper half and the upper valve seat and / or between the lower half and the lower valve seat. A ball-type seal surface separation mechanism is provided for separating the main valve body-side seal surface from the upper valve seat and / or the lower valve seat when the main valve body rotates.

  Preferably, the ball-type sealing surface separation mechanism includes a ball and a housing portion that accommodates the ball in a state in which a part of the ball protrudes in the vertical direction and is rotatable and substantially prevented from moving. The ball protruding from the housing portion so that the seal surface on the main valve body side is not separated from the upper valve seat and the lower valve seat before and after the main valve body starts rotating. And a concave hole having a size and shape so that the ball pushes down the upper half and rolls up while pushing up the lower half when the main valve body rotates. The ball and the accommodating portion are provided at two or more locations on the same circumference of the upper half portion and the lower half portion, and the concave hole is on the same circumference of the upper valve seat and the lower valve seat. The accommodation in plan view It said main valve body is provided in the angle component away rotating the flow channel switching from the same position and the position and.

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

  In addition, since the upper valve seat and the lower valve seat are flat, the valve seat surface can be made flat and smooth (the surface accuracy can be easily increased). The sealing performance can be remarkably improved as compared with a surface to be sealed that includes a cylindrical surface.

  Furthermore, 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 routed and the substantial occupied space including the piping can be reduced.

  Further, for example, by providing a ball-type seal surface separation mechanism, when the main valve body rotates (while the flow path is switched), the seal surface on the main valve body side is the valve seat surface of the upper valve seat or the lower valve seat. Since the sliding friction is hardly generated, stick slip or the like can be hardly generated, wear of the sliding portion can be greatly suppressed, and further, wear can be suppressed. As a result, sealing performance is improved and valve leakage can be effectively suppressed.

  In addition, by providing a foreign matter removing means comprising a leaf spring, when the main valve body rotates (while the flow path is switched), the seal surface on the main valve body side is the valve seat surface of the upper valve seat or the lower valve seat. Even after being separated from the upper valve seat and the lower valve seat by the elastic deformation (biasing force), part of the leaf spring provided on the upper end surface of the main valve body on the upper valve seat side and the lower end surface on the lower valve seat side Since it is pressed against the side valve seat and slides around the opening of each port in the valve seat surface of the upper valve seat or the lower valve seat in that state, it is possible to remove foreign matter present on or near the valve seat surface it can. Therefore, even when the main valve body side seal surface is pressed again against the valve seat surface of the upper valve seat or the lower valve seat at the end of rotation of the main valve body (after switching the flow path), the surfaces to be sealed Clogging of foreign matter between the two can be significantly suppressed, and also from this point, sealing performance is improved and valve leakage can be effectively suppressed.

  Furthermore, in the flow path switching valve of the present invention, the main valve body that receives the high pressure can be formed in a columnar shape, and a communication passage can be provided in the main valve body. High strength and durability.

  In addition to the above, when the flow path switching valve according to the present invention is used in an environment where a high-temperature and high-pressure refrigerant and a low-temperature and low-pressure refrigerant flow, such as a heat pump type air conditioning system, each communication path is relatively separated from the main valve body. Heat exchange in the main valve housing compared to the conventional type in which the high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant flow close to each other (a state in which one thin wall is separated). The amount can be greatly reduced, so that the efficiency of the system can be improved.

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

(A) is one side view in one Example of the flow-path switching valve concerning this invention, (B) is the upper surface side arrangement | positioning figure of the flow-path switching valve shown by (A), (C) is (A The arrangement | positioning figure of the lower surface side of the flow-path switching valve shown by FIG. The other side view partially fractured | ruptured according to the AA arrow line of FIG. 1 (B). The other side view which fractured | ruptured partially 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). The expanded sectional view with which the structure and operation | movement of a sealing surface separation mechanism and foreign material removal means provided in the flow-path switching valve of a present Example are provided. (A) is a figure with which it uses for description of the assembly method of the foreign material removal means shown by FIG. 5, (1) is the state before an assembly, (2) is an enlarged perspective view which shows the state after an assembly, respectively. (B) is a figure used for description of the assembly method of the other example of the foreign material removal means shown in FIG. 5, (1) is the state before assembly, (2) is the state after assembly, respectively. FIG. (A) shows the state which has a main valve body in a 1st rotation position in the flow-path switching valve of a present Example, (1) is an upper surface side arrangement | positioning figure, (2) is XX arrow of (1). Sectional view according to the line of sight, (B) shows a state in which the main valve body is in the second rotational position in the flow path switching valve of the present embodiment, (1) is a top side arrangement view, and (2) is (1). Sectional drawing according to a XX arrow line. (A) shows the state which the 1st layer member of the main valve body in a present Example exists in a 1st rotation position, (1) is a top view, (2) follows the XX arrow line of (1). Sectional drawing and (B) show the state in which the first layer member of the main valve body in the present embodiment is in the second rotational position, (1) is a plan view, and (2) is XX of (1). Sectional drawing which follows an arrow line of sight. (A) shows the state which the 2nd layer member of the main valve body in a present Example exists in a 1st rotation position, (1) is a top view, (2) follows the XX arrow line of (1). Sectional drawing and (B) show the state in which the second layer member of the main valve body in the present embodiment is in the second rotational position, (1) is a plan view, and (2) is XX in (1). Sectional drawing which follows an arrow line of sight. (A) shows the state which the 3rd layer member of the main valve body in a present Example exists in a 1st rotation position, (1) is a top view, (2) follows the XX arrow line of (1). Sectional drawing and (B) show the state in which the third layer member of the main valve body in the present embodiment is in the second rotational position, (1) is a plan view, and (2) is XX of (1). Sectional drawing which follows an arrow line of sight. (A) shows the state which the 4th layer member of the main valve body in a present Example exists in a 1st rotation position, (1) is a top view, (2) follows the XX arrow line of (1). Sectional drawing and (B) show the state in which the fourth layer member of the main valve body of the present embodiment is in the second rotational position, (1) is a plan view, and (2) is XX in (1). Sectional drawing which follows an arrow line of sight. The top view of the 1st layer member of the main valve body which shows the example which changed the arrangement composition of the foreign substance removal means of the main valve body in this example. The partial notch enlarged view of the lower part of FIG. 2 which shows the actuator part in one Example of the flow-path switching valve based on this invention. (A) is the elements on larger scale which show the principal part of the actuator shown by FIG. 13, (B) is a disassembled perspective view of the principal part of the motion conversion mechanism shown by (A). The schematic block diagram which shows an example of the rotation transmission mechanism used for the actuator shown by FIG. The schematic block diagram which shows the other examples of the rotation transmission mechanism used for the actuator shown by FIG. FIG. 14 is a diagram provided for explaining the operation of the actuator shown in FIG. 13. The four-way pilot valve with which the actuator shown by FIG. 13 is provided is shown, (A) is an expanded sectional view which shows the time of energization OFF, and (B) respectively shows the time of energization ON. The schematic block diagram which shows an example of a heat pump type | formula air conditioning system.

  Embodiments of the present invention will be described below with reference to the drawings.

  1A and 1B show an embodiment of a flow path switching valve according to the present invention, in which FIG. 1A is a side view, FIG. 1B is an upper surface arrangement diagram, and FIG. 2, 3, and 4 are other side views partially broken along the line AA in FIG. 1B, and other side views partially broken along the line BB, C It is an expanded sectional view of the main valve part which follows a -C arrow line.

  In the present specification, descriptions indicating positions, directions such as up and down, left and right, and front and rear are provided for the sake of convenience in accordance with the drawings in order to avoid complicated explanation, and are actually incorporated in a heat pump type air conditioning system or the like. It does not necessarily indicate the position and direction in the state of being pressed.

  In each drawing, the gap formed between the members, the separation distance between the members, etc. are larger than the dimensions of each constituent member for easy understanding of the invention and for convenience of drawing. Or it may be drawn small.

  The flow path switching valve 1 in 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 air conditioning system 100 shown in FIG. 19 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.

[Configuration and operation of main valve 5]
The main valve 5 includes a main valve housing 10 and a main valve body 20 disposed in the main valve housing 10 so as to be rotatable and vertically movable.

  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 a cylindrical body portion 10C and an upper surface opening of the body portion 10C, and further soldered and brazed. A thick disc-shaped upper valve seat 10A fixed by welding or the like, and a thick disc fixed to the trunk portion 10C in the same manner as the upper valve seat 10A so as to close the lower surface opening of the trunk portion 10C. A first valve 11 and a second port 12 made of pipe joints are provided vertically on the left and right sides of the upper valve seat 10A, and pipes are provided on the left and right sides of the lower valve seat 10B. A third port 13 and a fourth port 14 made of a joint are provided vertically. 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 and 17, respectively.

  In the present embodiment, when incorporated in the heat pump type air conditioning system 100 as shown in FIG. 19, for example, the first port 11 is a discharge side high-pressure port D connected to the compressor discharge side, and the second port 12 is an indoor input / output port E connected to the indoor heat exchanger, a third port 13 is an outdoor input / output port C connected to the outdoor heat exchanger, and a fourth port 14 is connected to the compressor suction side. A suction side low pressure port S (see FIG. 1).

  An upper rotary shaft portion 30A (described later) of the main valve body 20 is rotatably supported at the lower surface (inner surface) side center (on the center line O of the main valve housing 10) of the upper valve seat 10A in the main valve housing 10. A bearing hole 15A is provided. Further, in the vicinity of the center on the lower surface side of the lower valve seat 10 </ b> B, a concave portion 19 (a housing portion of a rotation transmission mechanism 70 described later) is provided downward, and the main valve body 20 is placed on the center line O in the concave portion 19. A bearing hole 15B that rotatably supports the lower rotary shaft portion 30B (described later) is provided.

  Further, the main body 50 and the pilot valve 80 of the actuator 7 are provided in the front and rear of the lower valve seat 10B. The main body 50 and the pilot valve 80 do not protrude 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 bifurcated configuration of a short columnar upper half 20A and a lower half 20B. Specifically, the upper half portion 20A is constituted by a relatively thick first layer member 21 and a second layer member 22 integrally joined to the lower surface side of the first layer member 21 by welding or the like, and is thick. The lower half portion 20B is composed of a disk-shaped third layer member 23 and a relatively thick fourth layer member 24 integrally joined to the lower surface side of the third layer member 23 by welding or the like. .

  Four compressions as urging means for urging the upper half 20A (second layer member 22) and the lower half 20B (third layer member 23) in opposite directions to each other The coil spring 29 is contracted (see FIG. 2). The four compression coil springs 29 are partly upward in four spring housing holes 23h (see FIG. 10) provided at equiangular intervals on the same circumference on the upper surface side of the third layer member 23. 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 of the main valve body 20 and the lower surface side of the fourth layer member 24. The upper half 20A and the lower half 20B of the main valve body 20 are integrally rotatable and vertically movable near both ends of the transverse grooves 27, 27. Therefore, as shown in FIG. 3, two through holes 26 are formed, and a stepped integral rotating rod 25 having small diameter portions 25 a at the upper and lower ends is inserted into the two through holes 26. Has been.

  As shown in FIGS. 2 to 4, the rotary shaft portion of the main valve body 20 is an upper rotary shaft portion 30 </ b> A that can behave integrally with the main body portion (the upper half portion 20 </ b> A and the lower half portion 20 </ b> B) of the main valve body 20. And the lower rotary shaft portion 30B, which are connected by the integrated rotary rod 25. The upper rotary shaft portion 30 </ b> A includes a pivot portion 30 a that is inserted into the bearing hole 15 </ b> A and a rectangular bar portion 30 b that has 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 bar portion 30d having a rectangular cross section that fits into the transverse groove 27, and an intermediate large diameter portion 30e. Insertion holes are provided near both ends of the square bar portions 30b and 30d, and small diameter portions 25a provided at the upper and lower end portions of the integral rotating rod 25 are inserted into the insertion holes by press-fitting or crimping. Thus, the integral rotating rod 25 is fixed to the upper rotating shaft portion 30A and the lower rotating shaft portion 30B.

  Therefore, the upper and lower rotary shaft portions 30A and 30B and the left and right integral rotating rods 25 and 25 constitute a frame-like body 28 assembled in a well shape or a rectangular shape so as to be integrally rotatable. 28, the main valve body 20 (upper half portion 20A, lower half portion 20B) that is divided into two parts is made to be slightly slidable along the integral rotating rod 25, so that its vertical movement, inclination, position Can flexibly cope with misalignment.

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

  When the main valve body 20 is in the first rotational position, the first communication path 31 for communicating the first port 11 and the third port 13 and the second port 12 for communicating the second port 12 and the fourth port 14 are provided. The communication path 32 is provided, and when the second rotational position is taken, the third communication path 33 and the third port 13 and the fourth port 14 are connected to communicate the first port 11 and the second port 12. A fourth communication path 34 is provided.

  Specifically, the upper surface opening or the lower surface opening of each passage portion provided in the first to fourth layer members 21 to 24 constituting the first to fourth communication passages 31 to 34 is the first to fourth ports. 11 to 14 are arranged on the same circumference, the diameter of each port is substantially the same as the diameter of each port 11 to 14, and the first communication path 31 and the second communication path 32 are connected to each port. The passage diameter is substantially the same as the diameter of 11-14.

  As shown in FIG. 8, the first layer member 21 constituting the upper part of the upper half 20A of the main valve body is provided with two straight through-passage portions 21A and 21B with an interval of 180 °, as well as the second Two lateral hole passage portions 21 </ b> C and 21 </ b> D connected by a horizontal hole 21 </ b> E having a planar view wave shape, the lower surface opening of which is closed by the layer member 22, are provided. The passage portions 21C and 21D with the horizontal holes are arranged with an interval of 180 °, and together, they form a U-shaped communication path with a relatively large volume (third communication path 33). The angle interval between the straight through passage portions 21A and 21B and the passage portions 21C and 21D with side 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 positioned 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 side holes are the first port 11 and the second port 12. Located directly below.

  As shown in FIG. 9, the second layer member 22 constituting the lower portion of the upper half 20A of the main valve body is provided with two straight through-passage portions 22A and 22B with an interval of 180 °. The straight through passage portions 22A and 22B are located directly below the straight through passage portions 21A and 21B of the first layer member 21.

  As shown in FIG. 10, the third layer member 23 constituting the upper part of the lower half 20B of the main valve body is provided with two linear through-passage portions 23A and 23B with an interval of 180 °. The straight through passage portions 23 </ b> A and 23 </ b> B are located directly below the straight through passage portions 22 </ b> A and 22 </ b> B of the second layer member 22.

  As shown in FIG. 11, the fourth layer member 24 constituting the lower part of the lower half 20B of the main valve body has two linear through-passage portions 24A spaced apart by 180 °, as in the first layer member 21. , 24B, and two side hole passage portions 24C, 24D connected by a horizontal hole 24E having a wave shape in plan view, the upper surface opening of which is closed by the third layer member 23. The straight through passage portions 24 </ b> A and 24 </ b> B are located directly below the straight through passage portions 23 </ b> A and 23 </ b> B of the third layer member 23. The passage portions 24C and 24D with the horizontal holes are arranged with an interval of 180 °, and together, they form a U-shaped communication path with a relatively large volume (fourth communication path 34). The angular interval between the straight through passage portions 24A and 24B and the passage portions 24C and 24D with lateral holes is 60 °.

  Therefore, when the main valve body 20 is in the first rotation position, the straight through-passage portions 24A and 24B are positioned immediately above the third port 13 and the fourth port 14, and the main valve body 20 is moved to the first rotation position. When rotating clockwise by 60 °, 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 side holes 24C, 24D with the third holes 13, 4 Located just above port 14.

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

  As can be understood by referring to FIGS. 4, 5 and 8, the valve seat surfaces 17 of the upper valve seat 10A and the lower valve seat 10B are provided at both ends of the communication passages 31, 32, 33 and 34 described above. , 17 are provided with a projecting portion 36 having annular sealing surfaces 37, 37 in close contact with the openings of the respective ports 11 to 14. Adjacent convex portions 36 and 36 (seal surfaces 37 and 37 thereof) are connected to form a spectacle shape in plan view, and the convex portions 36 (seal surfaces 37 of the fourth layer member 24) are provided. Is the same.

  Further, as shown in FIG. 4, the first communication passage 31 and the second communication passage 32 are divided communication passages that straddle the upper half 20A and the lower half 20B of the main valve body 20. In order to ensure sealing performance, the following measures are taken. That is, as a representative example of the first communication path 31, a large-diameter portion 22c is formed below the straight through-passage portion 22A of the second layer member 22 constituting the first communication path 31, and the third layer A cylindrical portion 23c is slidably inserted into the large diameter portion 22c at the upper end of the straight through-passage portion 23A of the member 23, and an O-ring 49 is interposed 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 path 32 has a similar configuration.

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

  The ball-type sealing surface separation mechanism 45 is provided between the first layer member 21 and the upper valve seat 10A, as shown in a representative example in FIGS. 46 in a state in which a part of the main body 46 protrudes in the vertical direction is rotatable and substantially prevented from moving, and before the rotation of the main valve body 20 is started and at the end of the rotation. When the main valve body 20 is rotated, a part of the ball 46 protruding from the housing 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. In the process of switching the flow path, the ball 46 is provided with an inverted conical concave hole 48 that is dimensioned so that the ball 46 rolls while pushing down the main valve body 20. The accommodating portion 47 includes a round hole 47a and a cylindrical stopper 47b that is fixed to the round hole 47 by press-fitting or the like and whose upper portion is narrowed.

  As shown in (1) of FIG. 8 and FIG. 11A, the accommodating portion 47 in which the ball 46 is accommodated is the same circle of the first layer member 21 and the fourth layer member 24 of the main valve body 20. The recesses 48 are provided at four locations on the circumference at intervals of 90 °, and the concave holes 48 are the same as the accommodating portion 47 in 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 8 positions, 60 degrees away from the position and clockwise from the position.

  In such a seal surface separation mechanism 45, before the rotation of the main valve body 20 and at the end of the rotation, as shown in FIG. 5A, a part of the ball 46 is placed in the recessed hole 48 of the upper valve seat 10A. It is inserted. This fitting amount (height from the valve seat surface 17 of the upper valve seat 10A to the top of the ball 46) is defined as h. When the main valve body 20 begins to rotate 60 ° from this state, the accommodating portion 47 moves (rotates) in the circumferential direction, and the ball 46 moves along with this, as shown in FIG. 20 (upper half portion 20A) rolls out of the recessed hole 48 while being pushed down against the urging 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 is separated from the valve seat surface 17 of the upper valve seat 10A. The amount by which the main valve body 20 is pushed down at this time is the fitting amount h.

  When the main valve body 20 is rotated by 60 °, the ball 46 is fitted into the next concave 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. The 20 sealing surfaces 37 are pressed against the valve seat surface 17 of the upper valve seat 10A.

  Further, in addition to the above, in the present embodiment, the main valve body between the first layer member 21 of the main valve body 20 and the upper valve seat 10A and between the fourth layer member 24 and the lower valve seat 10B. 20, around the opening of each of the ports 11 to 14 in the valve seat surfaces 17 and 17 of the upper valve seat 10 </ b> A and the lower valve seat 10 </ b> B, particularly in the vicinity of the opening of each of the ports 11 to 14. An annular seal surface 37 of the convex portion 36 provided at both ends of each communication passage 31, 32, 33, 34 of the body 20 (that is, the upper end surface of the first layer member 21 and the lower end surface of the fourth layer member 24). , 37 is provided for removing foreign matter existing (attached) in a portion in close contact with 37.

  The foreign matter removing means 40 basically has a length in the longitudinal direction as shown in FIG. 5 as a representative example provided between the first layer member 21 and the upper valve seat 10A. The diameter of the ports 11 to 14 (in other words, the diameter of the upper surface opening or the lower surface opening of each passage portion provided in the first to fourth layer members 21 to 24 constituting the first to fourth communication passages 31 to 34. ) Slightly longer, more specifically, greater than or equal to the outer diameter (seal diameter) of the annular seal surfaces 37, 37 provided around the upper surface opening or the lower surface opening of each passage portion (FIGS. 7, 8, 11). And a cross section (cross section perpendicular to the longitudinal direction) of a V-shaped leaf spring 41, a housing groove 42 having a size capable of housing a part or all of the leaf spring 41, and the leaf spring 41 are housed. A fixing member 43 for fixing to the groove 42 is provided. The material of the leaf spring 41 may be any material as long as it can withstand the pressure of the fluid to be introduced, such as metal or resin, but without inhibiting the rotation of the main valve body 20. Moreover, in order to prevent the valve seat surfaces 17 and 17 of the upper valve seat 10A and the lower valve seat 10B from being damaged, it is preferable to make them from Teflon (registered trademark) or the like having a low sliding resistance.

  Each storage groove 42 is formed on the upper surface of the first layer member 21 and the lower surface of the fourth layer member 24 of the main valve body 20 so as to extend in the radial direction of the main valve body 20 (FIGS. 7, 8, and FIG. 11), and a substantially concave shape in cross section (cross section perpendicular to the radial direction of the main valve body 20). Further, in the center of the bottom surface of each storage groove 42 in the circumferential direction, a notch 42 a having a triangular cross section is provided to position the leaf spring 41 with respect to the storage groove 42.

  Each of the storage grooves 42 communicates with the same port on the upper surface of the first layer member 21 and the lower surface of the fourth layer member 24 of the main valve body 20 before the rotation of the main valve body 20 and at the end of the rotation. It is formed between the communication paths. Specifically, as can be understood with reference to FIGS. 8 and 11, the upper end portion of the first communication passage 31 and the third communication passage 33 (the passage portion with a horizontal hole) are formed on the upper surface of the first layer member 21. 21C side (in the middle of the straight through-passage portion 21A and the upper surface opening of the passage portion 21C with a horizontal hole) and the upper end portion of the second communication passage 32 and the third communication passage 33 (horizontal hole). On the lower surface of the fourth layer member 24 of the main valve body 20 provided in the middle of the upper end portion (on the side of the passage portion 21D) (that is, in the middle of the straight through-passage portion 21B and the upper surface opening of the passage portion 21D with the horizontal hole). The middle between the lower end of the first communication passage 31 and the lower end of the fourth communication passage 34 (on the side of the passage portion 24C with a horizontal hole) (that is, between the straight through-passage portion 24A and the lower surface opening of the passage portion 24C with a horizontal hole) ), And the lower end of the second communication passage 32 and the fourth communication passage 34 (horizontal hole). Intermediate the can path of the 24D-side) the lower end (i.e., are provided in the middle) and the lower surface opening of the straight through passage portion 24B and the transverse bore walkway portion 24D. That is, the storage groove 42 is provided on the opposite side of the center line O of the main valve body 20 (with an interval of 180 °) on the upper surface of the first layer member 21 and the lower surface of the fourth layer member 24. The upper and lower surfaces are provided at the same position as viewed in the direction of the center line O.

  Here, as described above, among the convex portions 36 projecting from both ends of each communication passage 31, 32, 33, 34, adjacent convex portions 36, 36 (seal surfaces 37, 37 thereof) are continuously provided. Thus, the storage groove 42 is formed so that a part thereof overlaps the convex portion 36.

  When the above-described leaf spring 41 is assembled to the storage groove 42 provided in the first layer member 21 and the fourth layer member 24 of the main valve body 20, as shown in FIG. A fixing member 43 (in the illustrated example, a pentagonal cross section) that is equal to or slightly longer than the length (the length of the main valve body 20 in the radial direction) is prepared in advance, and the fixing member 43 is a V-shaped leaf spring. In the state where the top portion 41a of the leaf spring 41 is disposed in the portion defined by the top portion 41a of the 41 and the diverging leg portions 41b and 41b, the top portion 41a of the leaf spring 41 is aligned and fitted to the notch 42a of the storage groove 42 and fixed. The member 43 is press-fitted into the storage groove 42. As a result, the leaf spring 41 is placed and fixed in the storage groove 42 while being sandwiched between the storage groove 42 (the cut 42 a thereof) and the fixing member 43. In this case, the leaf spring 41 is fixed by adjusting the radial position in the storage groove 42 so as to be positioned from the inner side to the outer side of the outer end of the ports 11 to 14. In this state, a part of both leg portions 41b and 41b of the leaf spring 41 protrudes outward from the storage groove 42, more specifically, from the convex portion 36 (the seal surface 37).

  When the main valve body 20 assembled with the leaf spring 41 is disposed in the main valve housing 10, a part of both the leg portions 41 b and 41 b of the leaf spring 41 protruding from the storage groove 42 is formed on the upper valve seat 10 </ b> A and the lower valve. As shown in FIG. 5, a part or all of the leaf spring 41 is housed in the housing groove 42 in a state where it can be elastically deformed. That is, the leaf spring 41 constituting the foreign matter removing means 40 has a top portion 41a fixed to the upper end surface of the first layer member 21 between the main valve body 20 and the upper valve seat 10A, and both leg portions 41b, 41b. Is biased to the upper valve seat 10A side (upward), and between the main valve body 20 and the lower valve seat 10B, the top 41a is fixed to the lower end surface of the fourth layer member 24, Both leg portions 41b and 41b are in a state of being biased toward the lower valve seat 10B (downward).

  In the foreign matter removing means 40, before the rotation of the main valve body 20 and at the end of the rotation, as shown in FIG. 5 (A), it protrudes from both ends of each communication passage 31, 32, 33, 34. Since the annular sealing surface 37 of the convex portion 36 is in close contact with the openings of the ports 11 to 14 in the valve seat surfaces 17 and 17 of the upper valve seat 10A and the lower valve seat 10B, the leaf spring 41 is pressed. It is stored in the storage groove 42 in a deformed (elastically deformed) state. When the main valve body 20 starts to rotate 60 ° (clockwise or counterclockwise) from this state, the seal of the main valve body 20 is sealed by the seal surface separation mechanism 45 as shown in FIG. The surface 37 is separated from the valve seat surfaces 17 and 17 of the upper valve seat 10A and the lower valve seat 10B, but both the leg portions 41b and 41b of the leaf spring 41 accommodated in the accommodation groove 42 are on the upper valve seat 10A side (upward direction). ) And the lower valve seat 10B (downward), the leg portions 41b and 41b are pressed against the upper valve seat 10A and the lower valve seat 10B by elastic deformation (biasing force). At this time, the amount of deformation of the legs 41b and 41b in the vertical direction is the amount of fitting h. Then, when the main valve body 20 is further rotated, the leg portions 41b and 41b pressed against the upper valve seat 10A and the lower valve seat 10B are moved along with the upper valve seat 10A and the upper valve seat 10A. Around the openings of the ports 11 to 14 in the valve seat surfaces 17 and 17 of the lower valve seat 10B, in particular, the portions close to the annular sealing surfaces 37 and 37 of the convex portion 36 around the openings of the ports 11 to 14. Slide (see especially FIG. 8).

  When the main valve body 20 is rotated by 60 °, the sealing surface 37 of the main valve body 20 is again pressed against the valve seat surfaces 17 and 17 of the upper valve seat 10A and the lower valve seat 10B as described above. The spring 41 is housed in the housing groove 42 while being pressed and deformed (elastically deformed) by the upper valve seat 10A and the lower valve seat 10B.

  In the example shown in FIG. 6A, the fixing member 43 is fixed by press-fitting into the storage groove 42 with the leaf spring 41 sandwiched therebetween. For example, the fixing member 43 is fixed to the main valve body 20. (The first layer member 21 and the fourth layer member 24) are made of the same kind of material, and the length of the fixing member 43 is the length of the storage groove 42 (the length of the main valve body 20 in the radial direction). 6B, the end (the end in the radial direction of the main valve body 20) of the fixing member 43 (in the illustrated example, a rectangular cross section) You may fix by welding to the level | step difference part provided in the end surface in a radial direction.

  As understood from the above description, when the main valve body 20 takes the first rotational position, the first communication passage 31 that communicates the first port 11 and the third port 13 is the straight through passage portion 21A, The second communication path 32 that connects the second port 12 and the fourth port 14 is a straight through-passage portion 21B, 22B, 23B, and 24B. It becomes the linear path comprised.

  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 U-shaped passage formed of passage portions 21 </ b> C and 21 </ b> D with horizontal holes is provided, and a fourth communication passage 34 that connects the third port 13 and the fourth port 14 is provided in the lower half portion 20 </ b> B of the main valve body 20. It becomes a U-shaped passage composed of the passage portions 24C and 24D with the horizontal holes.

  As described above, in the flow path switching valve 1 of the present embodiment, the main valve body 20 is rotated 60 degrees clockwise from the first rotation position, so that the port 11-13 communicates with the first communication path 31. In addition, the flow path is switched from between the ports 12-14 communicating with the second communication path 32 to the ports 11-12 communicating with the third communication path 33 and between the ports 13-14 communicating with the fourth communication path 34. By rotating the main valve body 20 by 60 ° counterclockwise from the second rotation position, the ports 13-12 communicated by the third communication passage 33 and the ports 13-14 communicated by the fourth communication passage 34. The flow path is switched between the ports 11-13 communicating by the first communication path 31 and the ports 12-14 communicating by the second communication path 32.

  When the flow path switching valve 1 of this embodiment is incorporated into a heat pump type air conditioning system as shown in FIG. 19, as described above, for example, the first port 11 is connected to the discharge side of the compressor. The high-pressure port D, the second port 12 is an indoor input / output port E connected to the indoor heat exchanger, the third port 13 is an outdoor input / output port C connected to the outdoor heat exchanger, and the fourth port 14 is a compressor suction side The suction side low-pressure port S is connected to.

  When the cooling operation is performed, the main valve body 20 is set to the first rotational position as shown in FIG. As a result, as indicated by the white arrow in (2) of FIG. 7A, the high-pressure refrigerant from the compressor is discharged from the discharge-side 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 from the indoor-side inlet / outlet port 12 (E) to the linear second communication path 32 to the suction-side low-pressure port 14 (S).

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

[Function and effect of main valve 5]
In the flow path switching valve 1 of the present embodiment configured as described above, the first communication path 31 and the second communication path 32 have a thickness (passage diameter) from the start end to the end, and the first port 11 and the second connection path 32 have the same configuration. The straight passage is substantially the same as the diameter of the port 12, and the refrigerant flows straight down from the first port 11 and the second port 12, so that 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 constituted by the two lateral hole passage portions 21C and 21D, 24C and 24D have a relatively large internal volume, the pressure loss is reduced, and the total Thus, the pressure loss can be considerably reduced as compared with the conventional flow path switching valve.

  Further, the main valve body 20 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, and the upper half portion Since the compression coil spring 29 is mounted between 20A and the lower half portion 20B, the upper half portion 20A is pushed up by the spring force, and the sealing surface 37 of the upper half seat 20A on the valve seat surface 17 of the upper valve seat 10A. While being pressed around each port 11, 12, the lower half 20 </ b> B is pushed down and its sealing surface 37 is pressed around each port 13, 14 in the valve seat surface 17 of the lower valve seat 10 </ b> B.

  In this case, since the convex part 36 is protrudingly provided in the main valve body 20 (upper half part 20A and lower half part 20B) side, and the end surface is made into the annular seal surface 37, it is the part which contacts the valve seat surface 17 Area is minimized, so that the contact surface pressure is increased. Thereby, sufficient sealing performance can be ensured, and valve leakage in which fluid (refrigerant) leaks from the sliding surface of the main valve body 20 can be effectively suppressed.

  In addition, since the upper valve seat 10A and the lower valve seat 10B are formed in a flat plate shape, the valve seat surface 17 can be made flat and smooth (the surface accuracy can be easily increased). Compared with the case where the surface to be sealed includes a cylindrical surface, the sealing performance can be remarkably improved.

  Furthermore, since all the ports 11 to 14 are provided in the upper valve seat 10A and the lower valve seat 10B of the main valve housing 10, 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 20A of the main valve body 20 when the main valve body 20 rotates (during switching of the flow path) 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, there is almost no sliding friction. Therefore, stick-slip and the like can hardly occur, wear of the sliding part can be greatly suppressed, and further, since wear is suppressed, sealing performance is improved and valve leakage is effectively suppressed. be able to.

  Further, in the four-way switching valve having a conventional sliding main valve body as shown in Patent Document 1, the flow path opening area between the high pressure pipe D and the low pressure pipe S changes suddenly when the flow path is switched. An abnormal noise (switching noise) is generated by the fact that the high-pressure refrigerant is plunged into the low-pressure pipe. In order to prevent this abnormal noise, the frequency of the compressor is gradually reduced on the air conditioning system side so that the abnormal pressure due to the pressure difference between the high pressure pipe D and the low pressure pipe S is acceptable. It was necessary to switch the flow path. In the flow path switching valve 1 of this embodiment, the main valve body is switched from the valve seat surface by the amount h of engagement by the ball-type seal surface separation mechanism 45, so that the switching is performed after 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-mentioned abnormal noise can be suppressed. Further, by appropriately changing the fitting amount h, the degree of decrease in the compressor frequency at the time of switching the flow path can be made smaller than that of the air conditioning system using the four-way switching valve of Patent Document 1, and the frequency of the compressor It is also possible to switch the flow path without lowering.

  In the present embodiment, the foreign matter removing means 40 including the leaf spring 41 causes the seal surfaces 37, 37 on the main valve body 20 side to move to the upper valve seat 10A when the main valve body 20 rotates (while the flow path is switched). And the leaf spring 41 provided on the upper end surface on the upper valve seat 10A side and the lower end surface on the lower valve seat 10B side of the main valve body 20 even after being separated from the valve seat surfaces 17 and 17 of the lower valve seat 10B. The both leg portions 41b and 41b are pressed against the upper valve seat 10A and the lower valve seat 10B by elastic deformation thereof, and in this state, the ports 11 to 17 on the valve seat surfaces 17 and 17 of the upper valve seat 10A and the lower valve seat 10B. 14 slides around the 14 openings, so that foreign matters existing on the valve seat surfaces 17 and 17 or in the vicinity thereof can be removed. Therefore, at the end of the rotation of the main valve body 20 (after switching the flow path), the seal surfaces 37, 37 on the main valve body 20 side are again pressed against the valve seat surfaces 17, 17 of the upper valve seat 10A and the lower valve seat 10B. In this case as well, it is possible to greatly suppress the foreign matter between the surfaces to be sealed, and from this point, the sealing performance can be improved and the valve leakage can be effectively suppressed.

  Furthermore, in the flow path switching valve 1 of the present embodiment, the main valve body 20 (the upper half 20A and the lower half 20B) that receives high pressure is formed in a columnar shape, and the communication paths 31 to 34 are provided therein. Deformation (bending) or the like as in the conventional example hardly occurs, and sufficient strength and durability can be ensured.

  In addition to the above, when the flow path switching valve 1 of the present embodiment is used in an environment in which a high-temperature and high-pressure refrigerant and a low-temperature and low-pressure refrigerant are flowed, such as a heat pump air conditioning system, the communication passages 31 to 34 are connected to the main valve body 20. Compared to the conventional valve in which the high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant flow in close proximity (a state where a thin wall is separated), the main valve The amount of heat exchange in the housing can be greatly reduced, and the system efficiency can also be improved.

  In the above-described embodiment, the foreign matter removing means 40 has the same port on the upper surface of the first layer member 21 and the lower surface of the fourth layer member 24 of the main valve body 20 before the rotation of the main valve body 20 and at the end of the rotation. The ports 11 to 14 are formed in the valve seat surfaces 17 and 17 of the upper valve seat 10A and the lower valve seat 10B when the main valve body 20 rotates (when the flow path is switched). For example, as shown in FIG. 12, the same port before the rotation start of the main valve body 20 and at the end of the rotation is connected to the communication path. The foreign matter removing means 40 (along the radial direction of the main valve body 20) may be formed in a portion on the opposite side to the space between the communication passages communicating with each other. In FIG. 12, only the first layer member 21 is shown, but the fourth layer member 24 can be formed at the same position. That is, a total of twelve foreign matter removing means 40 may be formed, six on the first layer member 21 side and six on the fourth layer member 24. In the flow path switching valve 1 of the present embodiment, before the rotation of the main valve body 20 and at the end of the rotation, the seals of the convex portions 36 and 36 projecting from both ends of the communication passage not communicating with the ports 11 to 14 are provided. The surfaces 37 and 37 are also pressed against the valve seat surfaces 17 and 17 of the upper valve seat 10A and the lower valve seat 10B (portions other than those around the opening), but in the example shown in FIG. In this case, the foreign matter existing (attached) at that portion can be removed, so that the biting of the foreign matter between the main valve body 20 and the upper valve seat 10A and the lower valve seat 10B can be reliably suppressed. Also from this point, the sealing performance is improved and the valve leakage can be more effectively suppressed.

  In the above-described embodiment, when the main valve body 20 takes the first rotational position, the linear first communication path 31 that connects the first port 11 and the third port 13, the second port 12, and the second port 12 A linear second communication passage 32 that communicates with the four ports 14 is provided, and a U-shape that communicates the first port 11 and the second port 12 when the main valve body 20 assumes the second rotational position. The third communication passage 33 and the U-shaped fourth communication passage 34 for communicating the third port 13 and the fourth port 14 are provided, but the configuration of the four communication passages is limited thereto. For example, when the main valve body 20 takes the first rotational position, a linear first communication passage that allows the first port 11 and the third port 13 to communicate with each other, and the fourth port 14 and the second port. And a linear second communication passage that communicates with the main valve body 20. When the second rotational position is taken, a crank-shaped third communication path for communicating the first port 11 and the fourth port 14 and a crank-shaped fourth communication for communicating the third port 13 and the second port 12 are provided. It can also be set as the structure etc. which provide a channel | path. That is, at least one of the plurality of communication passages provided in the main valve body 20 is constituted by a linear passage as a whole, and the remaining at least one is constituted by a U-shaped or crank-shaped passage. You can also

  Further, in the above embodiment, the upper half portion 20A is composed 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 24 joined thereto. However, instead of that, the upper half portion 20A and the lower half portion 20B may be manufactured as a single unit from the beginning with a 3D printer or the like.

  Moreover, in the said Example, although the four-way switching valve 1 was illustrated, the flow-path switching valve based on this invention is not restricted to a four-way switching valve, It can apply also to a three-way switching valve etc. In the case of the three-way switching valve, in the flow path switching valve (four-way switching valve) 1 of the above embodiment, for example, the second port 12 provided in the main valve housing 10 is eliminated, and the first layer member 21 and the second layer member 21 are provided. The layer member 22 is integrated (because it is not necessary to form a U-shaped communication path (third communication path 33)), and the straight through-passage portion 21B constituting the second communication path 32 and the third communication path 33, It is good to delete 22B, 23B, 24B, the channel | path parts 21C and 21D with a side hole, and the part accompanying it.

  In addition, when using the said three-way switching valve for the heat pump type air conditioning system mentioned above, two said three-way switching valves are used, and it works as a four-way switching valve, or switching of a refrigerant | coolant or a cold / warm air supply destination (for example, Used to switch between sending to one of the two rooms or sending to the other).

[Configuration of Actuator 7]
Next, an example of the actuator 7 for rotating the main valve body 20 in the flow path switching valve 1 of the embodiment will be described with reference to FIGS. 13 to 18 in addition to FIG.

  The actuator 7 of the present embodiment is a fluid pressure type that utilizes a differential pressure between a high pressure fluid and a low pressure fluid that circulates in the main valve 5, and is provided on one end side of the lower valve seat 10 </ b> B in the main valve housing 10. The main body 50 is provided. The main body 50 is fixed by caulking and fixing so as to hermetically seal a cylindrical body 51 extending downward from the lower valve seat 10B and a lower surface opening of the body 51. , A lower surface closing member 52 having a convex portion 52a in the center, and a thick disk-shaped seal 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 An upper surface closing member 53 that also serves as a member and a stopper is provided, and a working chamber 55 is provided 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 short cylindrical rotation driving body 65 that is rotatably inserted with the pressure receiving moving body 60 in the vertical direction. Since the rotary drive body 65 is pivotally supported with respect to the main body 50, the rotary drive body 65 does not move in the vertical direction within the working chamber 55, but is relatively moved with the movement of the pressure receiving moving body 60 in the vertical direction. The pressure receiving moving body 60 is rotated (described in detail later).

  In the vicinity of the lower end of the outer periphery of the pressure-receiving moving body 60, a packing that hermetically seals between the inner peripheral surface of the working chamber 55 and hermetically partitions the working chamber 55 into a variable volume upper part 55A and a lower part 55B. 62, and an operating pin 63 that is fitted in a key groove 54 extending in the height direction provided at two left and right positions on the upper half of the inner periphery of the body 51. It is fixed by press fitting.

  The pressure receiving moving body 60 moves up and down linearly by the operating pin 63 and the key groove 54, but its rotation is prevented.

  FIG. 13 shows a state where the pressure receiving moving body 60 is at the lowest lowered position (down movement stroke completion state), and FIG. 14A shows a state where the pressure receiving moving body 60 is at the highest rising position (upper position). The movement stroke completion state) is shown (detailed later).

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

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

  Specifically, the pressure receiving moving body 60 is provided with a plurality of (two in the present embodiment) balls 72 and their accommodating portions 74, and the rotary drive body 65 is vertically moved around its outer periphery 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 is formed in a state where a part of the ball 72 protrudes radially inward by an upper end portion of the pressure receiving moving body 60 and an 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 where movement is substantially prevented, and the spiral groove 75 rotates with a part of a ball 72 protruding radially inward from the accommodating portion 74. It consists of a shallow groove with an arc-shaped cross-section that is in close contact.

  A rotation drive shaft portion 76 is caulked and fixed at the center of the rotation drive body 65 so as to rotate integrally with the rotation drive body 65. The rotation drive shaft portion 76 rotates in a lower large diameter portion 76a whose lower portion is fixed to the rotation drive body 65, an intermediate portion 76b following this, 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 that is freely supported. Further, the lower large-diameter portion 76a of the rotation drive shaft portion 76 has an insertion portion 76aa that is passed through the central hole of the rotation drive body 65 from the lower side, a diameter larger than that of the insertion portion 76aa, and the upper surface closing member 53. A first diameter-expanded portion 76ab that is passed through the central hole, and a second diameter-expanded portion 76ac that is further expanded than the first diameter-expanded 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 enlarged diameter portion 76ab.

  A downward step surface formed by the first enlarged portion 76ab and the second enlarged portion 76ac and the upper surface of the upper surface closing member 53 come into contact with each other, so that the rotational drive shaft portion 76 and the rotational drive fixed thereto are brought into contact. The body 65 is prevented from falling off, and the downward step surface formed by the insertion portion 76aa and the first enlarged diameter portion 76ab is used when the rotary drive body 65 is caulked and fixed to the rotary drive shaft portion 76. It is regarded as a receiving surface.

  Here, the rotation axis Q (rotation 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 in parallel to the rotation axis O of the main valve body 20. A rotation transmission mechanism 77 that transmits the rotation of the rotation drive body 65 to the main valve body 20 is provided between the rotation drive shaft section 76 and the lower rotation shaft section 30B of the main valve body 20.

  The rotation transmission mechanism 77 has a base end portion connected and fixed to the intermediate portion 76b of the rotation drive shaft portion 76, as can be understood by referring to FIG. 15 in addition to FIGS. 13 and 14A. The base end portion is connected and fixed to the drive arm 78 having a U-shaped engagement groove 78a formed in the main valve body 20 and the pivot portion 30c of the lower rotary shaft portion 30B of the main valve body 20, and the U-shape is located near the distal end thereof. An engaging pin 79 that slidably engages with the engaging groove 78a is constituted by a driven arm 39 that hangs downward.

  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 therewith, and accordingly, the vicinity of the tip of the driven arm 39 (engagement pin 79) is driven. Along with the vicinity of the tip of the arm 78 (U-shaped engagement groove 78a), the lower rotary shaft 30B and the main valve body 20 are rotated. In this case, in this embodiment, the rotation angle θ of the driven arm 39 is 60 °, and is the rotation angle that the main valve body 20 needs to switch the flow path as described above. The rotation angle θ is set by the stroke length of the vertical movement of the pressure receiving moving body 60, the lever ratio (leverage ratio) of the drive arm 78 and the driven arm 39, and the like. Note that FIGS. 13, 14A, and FIGS. 17A to 17D, which will be described later, show a state where the drive arm 78 and the driven arm 39 are rotating.

  As shown in FIG. 16, the rotation transmission mechanism includes 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 meshing with the drive gear 97. You may comprise with the gear 98, etc.

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

  13 and 17A show a state in which high pressure fluid (high pressure refrigerant) is introduced into the working chamber upper portion 55A through the upper port 56 and discharged from the working chamber lower portion 55B through the lower port 57. Show. When the high-pressure fluid is introduced into the working chamber upper portion 55A, the high-pressure fluid reaches the corners of the space (the working chamber upper portion 55A) above the packing 62 attached to the pressure receiving moving body 60 and below the 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 through 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, or the main body 50 The pressure receiving area on the upper surface side of the pressure receiving moving body 60 is equal to the pressure receiving area on the lower surface side of the pressure receiving moving body 60.

  Under such a configuration, in the state shown in FIGS. 13 and 17A, high-pressure fluid is introduced into the working chamber lower portion 55B through the lower port 57, and the upper port 56 is connected to the working chamber upper portion 55A. When the high-pressure fluid is discharged via the pressure chamber, the pressure in the lower working chamber 55B becomes higher than that in the upper working chamber 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. As a result, the pressure receiving moving body 60 moves straight up, and the ball 72 of the motion conversion mechanism 58 also moves straight 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 rotation driving body 65 rotates in one direction (here, clockwise). Then, when the upper end (annular pressing member 66) of the pressure receiving moving body 60 comes into contact with the upper surface closing member 53, the upward movement of the pressure receiving moving body 60 is stopped and the rotation of the rotation driving body 65 is also stopped. Hereinafter, this stroke is referred to as an upward movement stroke, and the state shown in FIG. 17B (the state where the pressure receiving moving body 60 is at the highest position) is referred to as an upward movement stroke completion state.

  On the other hand, as shown in FIGS. 17C and 17D, in the state where the upward movement stroke is completed, high pressure fluid is introduced into the upper part of the working chamber 55A through the upper port 56, and the lower part from the lower part of the working chamber 55B to the lower part. When the high-pressure fluid is discharged through the port 57, the working chamber upper portion 55A has a higher pressure than the working chamber lower portion 55B, so that the pressure receiving moving body 60 is pushed downward, and the operating pin 63 of the pressure receiving moving body 60 is moved to the key groove. While being guided by 54, the pressure receiving moving body 60 moves down straight, and accordingly, the ball 72 of the motion conversion mechanism 58 also moves down straight while rotating. At this time, the spiral groove 75 is pushed in the circumferential direction by the portion of the ball 72 that is fitted in the spiral groove 75, and the rotational driving body 65 rotates in the other direction (counterclockwise here). When the lower end of the pressure receiving moving body 60 comes into contact with 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 rotation driving body 65 is also stopped. Hereinafter, this stroke is referred to as a downward movement stroke, and the state shown in FIG. 17D (the state where the pressure receiving moving body 60 is at the lowest lowered position) is referred to as a downward movement stroke completion state.

  By causing the pressure receiving moving body 60 to take the downward movement stroke in the state of completion of the upward movement stroke, 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 the upward movement stroke in the state where the downward movement stroke is completed, the main valve body 20 rotates from the second rotation position to the first rotation position. The flow path is switched as described above.

  In the present embodiment, the flow path switching, that is, the switching between the upward movement stroke and the downward movement stroke, is performed in the upper port 56 and the lower port 57 and in the main valve housing 10 which is a high pressure portion and in the low pressure portion. The operation is performed by an electromagnetic four-way pilot valve 80 connected to the 4 port 14 (suction side low pressure port S).

[Configuration and operation of electromagnetic four-way pilot valve 80]
The structure of the four-way pilot valve 80 is well known. As shown in FIG. 18, the four-way pilot valve 80 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. A cylindrical valve case portion 81 having a lower surface opened downward toward the side (that is, near the center rear side of the lower surface side of the lower valve seat 10B), and the lower surface opening of the valve case portion 81 are airtight. A solenoid part 82 fixed by brazing, caulking or the like so as to be sealed, and an inner end face of the valve case part 81 that is hermetically attached to the side surface part of the valve case part 81 by press-fitting or caulking or the like. ) 92 and has a bottomed cylindrical valve seat block 83 that serves as a stopper that restricts movement of the plunger 85 in a direction away from the suction element 84 of the plunger 85.

  The inside of the valve case portion 81 is a valve chamber 88. The valve chamber 88 communicates with 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 part 82 includes a coil 82a for energization excitation, a cover case 82b covering the outer periphery of the coil 82a, an attractor 84 disposed on the inner peripheral side of the coil 82a and fixed to the cover case 82b by a bolt 82c, A plunger 85 or the like disposed opposite to the child 84 is provided. The plunger 85 is slidably fitted into a cylindrical guide pipe 86 having a lower portion disposed between the coil 82a and the attractor 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 hook-like portion is airtightly attached to the valve case portion 81 by welding, brazing, caulking or the like.

  A compression coil spring 87 that biases the plunger 85 in a direction away from the suction element 84 (upward in the drawing) is mounted between the suction element 84 and the plunger 85.

  A valve body holder 90 that holds the valve body 91 slidably in the thickness direction on the free end side of the plunger 85 on the side opposite to the suction element 84 side is caulked by the wide base end portion 96. It is fixed. A leaf spring 94 that urges the valve body 91 in a direction (thickness direction) to press the valve body 91 against the valve seat 92 is attached to the valve body holder 90. The valve body 91 slides on the seat surface of the valve seat 92 as the plunger 85 moves up and down.

  The valve seat 92 is provided with a port a, a port b, and a port c in order from the top, and the valve body 91 selectively communicates the port a with the port b and the port b with the port c. A recessed portion 93 is provided which is obtained and is recessed in the thickness direction. The valve seat block 83 has one end portion of the narrow tube 95a communicating with only the port a, one end portion of the thin tube 95b communicating with only the port b, and one end portion of the narrow tube 95c communicating with only the port c. Are inserted in an airtight manner.

  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 working chamber lower part 55B via the lower port 57 of the main body part 50.

  In the four-way pilot valve 80 configured as described above, when the energization to the solenoid portion 82 is turned off, as shown in FIG. It is pushed up to a position where it abuts against the seat block 83. In this state, the valve body 91 is positioned on the port a and the port b, and the port a and the port b communicate with each other by the concave portion 93, and the port c and the valve chamber 88 communicate with each other. The high pressure fluid is introduced into the working chamber lower portion 55B through the pore 89 → the valve chamber 88 → the port c → the narrow tube 95c → the lower port 57, and the high pressure fluid in the upper portion of the working chamber 55A is transferred to the upper port 56 → the narrow tube 95a → port a. → The recess 93 → the port b → the narrow tube 95 b → the fourth port 14 (the suction side low pressure port S) is discharged.

  On the other hand, when the energization of the solenoid portion 82 is turned on, the plunger 85 is pulled to a position where the lower end of the plunger 85 comes into contact with the suction element 84 by the suction force of the suction element 84 as shown in FIG. At this time, the valve body 91 is positioned on the port b and the port c, and the port b and the port c communicate with each other by the concave portion 93, and the port a and the valve chamber 88 communicate with each other. The fluid is introduced into the working chamber upper part 55A via the pore 89 → the valve chamber 88 → the port a → the thin tube 95a → the upper port 56, and the high-pressure fluid in the lower part of the working chamber 55B is transferred to the lower port 57 → the narrow tube 95c → port c → It flows out from the concave portion 93 → 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 movement stroke is taken, the main valve body 20 rotates from the second rotation position to the first rotation position, and the flow path switching as described above is performed. On the other hand, when energization to the solenoid unit 82 is turned ON, the downward movement 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. Switching is performed.

[Function and effect of actuator 7]
As described above, in the flow path switching valve 1 of the present embodiment, the pressure difference between the high pressure fluid and the low pressure fluid flowing through the main valve 10 is switched by switching the energization to the electromagnetic four-way pilot valve 80 on and off. Since the main valve body 20 is rotated by using the motor, cost reduction, power consumption reduction, energy saving, and the like are achieved as compared with the case where the main valve body 20 is rotated by an electric motor or the like. Can do. Note that the flow path switching by the actuator 7 of this embodiment can be performed more quickly than the flow path switching performed by the electric motor and the speed reducer.

  In the above embodiment, in order to simplify the configuration, the rotation transmission mechanism 77 of the actuator 7 is omitted, and the drive shaft portion of the rotation drive body 65 and the rotation shaft portion of the main valve body 20 are arranged on a common axis. Thus, the main valve body 20 and the rotary drive body 65 may be rotated integrally. That is, the rotary drive body 65 may be externally fitted and fixed to the lower rotary shaft portion 30B of the main valve body 20 by press fitting, caulking, or the like so that the rotation of the rotary drive body 65 is directly transmitted to the main valve body 20. .

  In the above embodiment, the four-way pilot valve 80 is used to switch the flow path by selectively introducing and discharging the high-pressure fluid to the working chamber upper portion 55A and the working chamber lower portion 55B. However, the present invention is not limited to this. For example, a pressure equalizing passage is provided in the working chamber, and high pressure fluid is introduced into the entire working chamber through the pressure equalizing passage, and a high pressure from the working chamber to the low pressure portion of the main valve The discharge of the fluid may be selectively performed through either the upper port or the lower port by a three-way pilot valve, so that the lower movement stroke and the upper movement stroke, that is, the flow path switching may be performed.

  Of course, the flow path switching valve according to the present invention can be incorporated not only in the heat pump air conditioning system but also in other systems, devices, and devices.

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

DESCRIPTION OF SYMBOLS 1 Flow path switching valve 5 Main valve 7 Actuator 10 Main valve housing 10A Upper valve seat 10B Lower valve seat 11 1st port 12 2nd port 13 3rd port 14 4th port 17 Valve seat surface 20 Main valve body 20A Upper half Part 20B Lower half part 21 First layer member 22 Second layer member 23 Third layer member 24 Fourth layer member 27 Transverse groove 29 Compression coil spring 30A Upper rotary shaft part 30B Lower rotary shaft part 31 First communication path 32 First 2 communication path 33 3rd communication path 34 4th communication path 36 Convex part 37 Seal surface 40 Foreign substance removal means 41 Leaf spring 42 Storage groove 43 Fixing member 45 Ball type seal surface separation mechanism 50 Main part 52 of actuator Lower surface closing member 53 Upper surface Blocking member 54 Key groove 55 Working chamber 55A Working chamber upper portion 55B Working chamber lower portion 56 Upper port 57 Lower port 58 Motion conversion mechanism 60 Pressure receiving moving body 62 Packing 63 Actuating pin 65 Rotation drive body 72 Ball 75 Spiral groove 76 Rotation drive shaft part 77 Rotation transmission mechanism 80 Four-way pilot valve 82 Solenoid part 83 Valve seat block 85 Plunger 88 Valve chamber 89 Fine hole 90 Valve body holder 91 Valve body 92 Valve Seat 93 Recesses a, b, c Port (4-way pilot valve)
95a, 95b, 95c Narrow tube D High pressure port on the discharge side S Low pressure port on the suction side C Outer port / outlet port E Indoor port / out port

Claims (9)

At least three cylinder main valve housings whose upper and lower opening are hermetically sealed by the upper valve seat and the lower valve seat, the upper valve seat and / or the lower valve seat are provided in total. A main valve having a main valve body that is rotatably disposed in the main valve housing and is provided with a plurality of communication passages for selectively communicating between the ports; An actuator for switching between ports communicating by rotating the valve body,
When the main valve body is rotated between the main valve body and the upper valve seat and / or between the main valve body and the lower valve seat, the seal surface on the main valve body side is used as the upper valve seat. A seal surface separation mechanism for separating the seat and / or the lower valve seat, and a part thereof are fixed to the upper end surface of the main valve body on the upper valve seat side and / or the lower end surface of the lower valve seat side. The other portion is a leaf spring biased toward the upper valve seat and / or the lower valve seat, and the other portion of the leaf spring is elastically deformed when the main valve body rotates. The valve seat slides around the opening of the port in the valve seat surface of the upper valve seat and / or the lower valve seat while being pressed against the upper valve seat and / or the lower valve seat by Remove foreign objects present on or near the surface Flow path switching valve, wherein a and objects removal means are provided.   The flow path switching valve according to claim 1, wherein the leaf spring of the foreign matter removing means is fixed to a storage groove formed on an upper end surface and / or a lower end surface of the main valve body.   At both ends of the communication path, convex portions having annular sealing surfaces that are in close contact with the openings of the ports in the upper valve seat and / or the lower valve seat protrude, and the storage groove includes at least The flow path switching valve according to claim 2, wherein a part of the flow path switching valve is formed so as to overlap the convex portion.   The leaf spring is provided along the radial direction of the main valve body, and at least the annular portion of the convex portion around the port opening in the valve seat surface of the upper valve seat and / or the lower valve seat. 4. The flow path switching valve according to claim 3, wherein the size and shape are set so that the seal surface slides in close contact with the seal surface.   The leaf spring has a V-shape when viewed in a cross section perpendicular to the radial direction of the main valve body, the top thereof is fixed to the upper end surface and / or the lower end surface of the main valve body, and the both leg portions thereof are 5. The flow path switching valve according to claim 4, wherein the flow path switching valve is biased toward the upper valve seat side and / or the lower valve seat side.   6. The flow according to claim 1, wherein the leaf spring is disposed between the communication passages communicating with the port before the rotation of the main valve body and at the end of the rotation. Road switching valve.   The leaf spring is also disposed on the opposite side of the communication passage from the communication passage communicating with the port before the rotation of the main valve body and at the end of the rotation. The flow path switching valve according to claim 6. The main valve body is configured to be divided into an upper half part and a lower half part that are integrally rotatable and vertically movable, and the upper half part and the lower half part are opposite to each other. A biasing means for biasing is interposed,
When the main valve body is rotated between the upper half part and the upper valve seat and / or between the lower half part and the lower valve seat, the seal surface on the main valve body side is placed on the upper valve. The flow path switching valve according to any one of claims 1 to 7, further comprising a ball-type seal surface separation mechanism for separating the seat and / or the lower valve seat. The ball-type sealing surface separation mechanism includes a ball, a housing portion that accommodates the ball in a state in which a part of the ball protrudes in the vertical direction, and is rotatable and substantially prevented from moving. Before starting the rotation of the valve body and at the end of the rotation, a part of the ball protruding from the housing portion so that the seal surface on the main valve body side is not separated from the upper valve seat and the lower valve seat. And when the main valve body rotates, a concave hole having a size and shape so that the ball pushes down the upper half and rolls up while pushing up the lower half, and the ball and The housing 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, as seen in a plan view. At the same position as the receiving part Flow path switching valve according to claim 8, characterized in that the main valve body is provided at an angle component away rotating the flow channel switching from fine said position.

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