JP6453040B2 - 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 air conditioning system equipped 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 arrow in FIG. 24, the discharge side of the flow path switching valve 140 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 Fluid pressure type actuator that utilizes the pressure difference between the high-pressure refrigerant and low-pressure refrigerant in the system (two separated by a plate-like body that is cantilevered on the extension shaft part of the rotary shaft part of the plate-like main valve body) This is done by selectively introducing and discharging high-pressure refrigerant into the working chamber using 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 hydraulic pressure actuator for rotating the main valve body (flow path switching) is such that the portion that receives the high pressure is the rotation shaft portion of the main valve body. Since it is a plate-like body that is cantilevered on the extension shaft and has a large pressure receiving area with respect to the plate thickness, deformation (bending) is likely to occur, there is a problem in strength and durability, and channel switching is reliable. I hate lacking in sexuality and quickness.

  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. In addition to ensuring sufficient strength to withstand high pressure and improving durability, it is possible to switch the flow path reliably and quickly, and in high-temperature and high-pressure environments such as heat pump air conditioning systems. It is to provide a flow path switching valve that can be incorporated.

In order to achieve the above object, a flow path switching valve according to the present invention basically includes a main valve housing and a main valve including a main valve body rotatably disposed in the main valve housing, A fluid pressure type actuator for rotating the main valve body, the flow path is switched by rotating the main valve body, and the actuator is a high-pressure fluid supplied to the main valve. And a motion converting mechanism for converting a reciprocating linear motion into a rotational motion in both forward and reverse directions using the pressure of the high-pressure fluid is provided in the working chamber. The movement converting mechanism is configured such that the pressure receiving moving body accommodated in the working chamber so as to be able to move up and down in a state in which the rotation thereof is blocked, and to be relatively rotatable corresponding to the vertical movement of the pressure receiving moving body. Rotating drive that is inserted or extrapolated into the pressure-receiving moving body The ball and the ball are accommodated in one of the pressure-receiving moving body and the rotational drive body in a state where a part of the ball protrudes in the radial direction, and the movement is substantially prevented. a housing portion is provided, on the other hand, a portion of the ball projects radially from the receiving portion is fitted, the structure der Rukoto the helical grooves extending in the vertical direction while bending in the circumferential direction are provided It is a feature.

  In a preferred aspect, a packing is provided on the outer periphery of the pressure receiving moving body so as to hermetically seal a space between the inner peripheral surface of the working chamber and partition the working chamber into a variable volume upper and lower portions, An upper port for introducing and discharging high-pressure fluid is provided in the upper portion of the working chamber, and a lower port for introducing and discharging high-pressure fluid is provided in the lower portion of the working chamber.

  The actuator preferably introduces the high-pressure fluid into the lower portion of the working chamber via the lower port and discharges the high-pressure fluid from the upper portion of the working chamber via the upper port, thereby raising the pressure-receiving movable body. An upper stroke of rotating the rotary drive body in one direction, and introducing high-pressure fluid into the upper portion of the working chamber via the upper port, and supplying high-pressure fluid from the lower portion of the working chamber via the lower port. By discharging, the pressure receiving movable body is moved downward to selectively take a downward stroke in which the rotary drive body is rotated in the other direction.

   In another preferred embodiment, switching between the upper stroke and the lower stroke is performed by a four-way pilot valve connected to the upper port and the lower port, and a high pressure portion and a low pressure portion in the main valve. To be done.

  The rotation axis of the rotary drive body is preferably eccentric with respect to the rotation axis of the main valve body and is arranged in parallel to the rotation axis of the main valve body.

  In another preferred aspect, a rotation transmission mechanism for transmitting the rotation of the rotary drive body to the main valve body is provided between the rotary drive body of the actuator and the main valve body.

  Preferably, the rotation transmission mechanism is connected and fixed to a drive shaft connected to the drive shaft portion of the rotary drive body, and connected to the rotary shaft portion of the main valve body, and the vicinity of the tip thereof is close to the tip of the drive arm. It is composed of a driven arm that is rotated.

  Preferably, the rotation transmission mechanism includes a drive gear connected and fixed to the drive shaft portion of the rotary drive body, and a driven gear connected and fixed to the rotary shaft portion of the main valve body and meshing with the drive gear. Is done.

  In another preferred aspect, the drive shaft portion of the rotary drive body and the rotary shaft portion of the main valve body are disposed on a common axis, and the main valve body and the rotary drive body rotate integrally. To be done.

  In the flow path switching valve according to the present invention, the main valve body is rotated by a fluid pressure type actuator that uses the differential pressure between the high pressure fluid and the low pressure fluid flowing through the main valve. Compared with the case where the main valve body is rotated, the cost, power consumption, and energy saving can be reduced, and pressure loss and sliding part wear can be achieved compared to the slide type. As a result, the sealing performance can be improved and the valve can hardly leak.

  In addition, the actuator that rotates the main valve body is configured to move the pressure-receiving moving body up and down by fluid pressure, convert this up-and-down movement into a rotational motion, and transmit it to the main valve body. Compared to the part that is cantilevered by the extension shaft part of the rotating shaft part of the main valve body and has a large pressure receiving area relative to the plate thickness, the part that receives high pressure (pressure receiving moving body) Sufficient strength can be ensured, durability can be improved, and sufficient strength can be ensured, so that the pressure receiving area can be increased, and therefore the flow path can be switched reliably and quickly.

  As a mechanism for converting linear motion into rotational motion, a ball screw mechanism is generally known. However, since a normal ball screw mechanism uses a large number of balls and requires a return structure, the motion of the present invention is also known. Compared to the conversion mechanism, the structure is complicated and expensive, and use in a high-temperature and high-pressure environment is not considered. Therefore, it is difficult to employ it for a flow path switching valve incorporated in a heat pump air conditioning system or the like. On the other hand, the fluid pressure type actuator provided with the motion conversion mechanism of the present invention has an extremely simple configuration with a small number of parts, so that it is advantageous in terms of cost and measures for use in a high temperature and high pressure environment (pressure receiving) For example, the flow path switching valve according to the present invention can be used as a flow path switching valve incorporated in a high-temperature and high-pressure environment such as a heat pump type air conditioning system. It is extremely cost effective.

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

(A) is a side view in the first embodiment of the flow path switching valve according to the present invention, (B) is a top side layout diagram of the flow path switching valve shown in (A), (C) is ( The lower surface side arrangement drawing of the flow-path switching valve shown to A). 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 description of the seal surface separation mechanism provided in the flow-path switching valve of 1st Example are provided. (A) shows the state in which the main valve body is in the first rotational position in the flow path switching valve of the first embodiment, (1) is a top surface arrangement diagram, and (2) is XX of (1). A sectional view taken along the line of sight, (B) shows a state where the main valve body is in the second rotational position in the flow path switching valve of the first embodiment, (1) is a top side arrangement view, and (2) is ( Sectional drawing which follows the XX arrow line of 1). (A) shows the state in which the first layer member of the main valve body in the first embodiment is in the first rotational position, (1) is a plan view, and (2) is a view taken along line XX in (1). (B) shows a state in which the first layer member of the main valve body in the first embodiment is in the second rotational position, (1) is a plan view, and (2) is X in (1). -Sectional drawing which follows a X arrow line of sight. (A) shows the state in which the second layer member of the main valve body in the first embodiment is in the first rotational position, (1) is a plan view, and (2) is a view taken along the line XX of (1). (B) shows a state in which the second layer member of the main valve body in the first embodiment is in the second rotational position, (1) is a plan view, and (2) is an X of (1). -Sectional drawing which follows a X arrow line of sight. (A) shows the state which has the 3rd layer member of the main valve body in the 1st example in the 1st rotation position, (1) is a top view, (2) is a XX arrow line of (1). (B) shows a state in which the third layer member of the main valve body in the first embodiment is in the second rotational position, (1) is a plan view, and (2) is X in (1). -Sectional drawing which follows a X arrow line of sight. (A) shows the state in which the 4th layer member of the main valve body in the 1st example is in the 1st rotation position, (1) is a top view, (2) is a XX arrow line of (1). (B) shows a state in which the fourth layer member of the main valve body of the first embodiment is in the second rotational position, (1) is a plan view, and (2) is an X of (1). -Sectional drawing which follows a X arrow line of sight. The example which made the upper half part and the lower half part of the main valve body of 1st Example integrated respectively is shown, (A) is in the state in the 1st rotation position, (B) is in the 2nd rotation position. Sectional drawing which shows a state, respectively. The example which made the upper half part and lower half part of the main valve body of 1st Example integrated is shown, (A) is in the state in the 1st rotation position, (B) is in the state in the 2nd rotation position Sectional drawing which shows each. The flow-path switching valve of 2nd Example is shown, (A) shows the state in which the main valve body exists in the 1st rotation position, (B) rotates the main valve body 90 degrees clockwise from the 1st rotation position. 2 is a top view of the arrangement, (2) is a schematic diagram showing the configuration of the communication path in each state, and (3) is a bottom view. (A) is (1) 1st layer member, (2) 2nd layer member, (3) 3rd layer member in the state which has the main valve body in 2nd Example in a 1st rotation position, (4) ) Each plan view of the fourth layer member, (B) shows the communication path configuration in the state where the main valve body is in the first rotation position, (B) (1) ~ (4) is (A) Sectional drawing which follows the XX arrow line of (1)-(4). (A) is (1) 1st layer member, (2) 2nd layer member, (3) 3rd layer member in the state which has the main valve body in 2nd Example in a 2nd rotation position, (4) ) Each plan view of the fourth layer member, (B) shows the communication path configuration in a state in which the main valve body is in the second rotational position, (B) (1) upper side, lower side, (A) (1) in U1 U line of sight, VV arrow line of partial cross-sectional view, (B) (2) and (3) of (A) (2) and (3) Sectional drawing according to YY arrow line, (B) (4) upper side and lower side are respectively JJ arrow line and (KK) arrow line in (4) of (A). The flow-path switching valve of 3rd Example is shown, (A) is the state which has a main valve body in a 1st rotation position, (B) is the state which has a main valve body in a 2nd rotation position, (1 ) Is a top surface side arrangement view, and (2) is a cross-sectional view taken along the line XX of (1). The partial notch enlarged view of the lower part of FIG. 2 which shows the actuator part in 1st Example of the flow-path switching valve based on this invention. (A) is the elements on larger scale which show the principal part of the actuator shown by FIG. 17, (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 example of the rotation transmission mechanism used for the actuator shown by FIG. FIG. 18 is a diagram which is used for explaining the operation of the actuator shown in FIG. 17. FIG. 18 is an enlarged cross-sectional view illustrating a four-way pilot valve provided in the actuator illustrated in FIG. The partial notch enlarged view which shows the other Example of the flow-path switching valve concerning this invention. 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 a first embodiment of a flow path switching valve according to the present invention, in which FIG. 1A is a side view, FIG. 1B is a top view, and FIG. 1C is a bottom view. 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.

[First embodiment of main valve]
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. 24 described above. And a pressure type actuator 7.

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

  The main valve 5 includes a main valve housing 10 and a main valve body 20 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 a heat pump type air conditioning system 100 as shown in FIG. 24, 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).

  A bearing hole 15A that rotatably supports an upper rotary shaft portion 30A (described later) of the main valve body 20 is provided at the lower surface side center of the upper valve seat 10A in the main valve housing 10 (on the center line O of the main valve housing 10). In the vicinity of the center of the lower surface side of the lower valve seat 10B, a concave portion 19 (a housing portion for a rotation transmission mechanism 70 described later) is provided downward. A bearing hole 15B that rotatably supports a lower rotating shaft portion 30B (described later) of the valve body 20 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. 9) provided at equal angular intervals on the same circumference on the upper surface side of the third layer member 23. It is loaded in 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 25a 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. 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 the small-diameter portions 25a provided at the upper and lower ends of the integral rotation rod 25 are fitted into the insertion holes. The rod 25 is fixed to the upper rotary shaft portion 30A and the lower rotary shaft portion 30B.

  Therefore, the upper and lower rotary shaft portions 30A and 30B and the left and right 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 slightly movable relative to each other and integrally rotatable. Thus, the frame-like body 28 can flexibly cope with vertical movement, inclination, positional deviation, and the like of the main valve body 20 (upper half 20A, lower half 20B) having a two-part configuration.

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

  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. 7, 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. 8, the second layer member 22 constituting the lower part 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. 9, the third layer member 23 that forms 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. 10, the fourth layer member 24 that forms 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 with reference to FIGS. 4, 5, and 7, the valve seat surfaces 17 of the upper valve seat 10 </ b> A and the lower valve seat 10 </ b> B are provided at both ends of each of the communication passages 31, 32, 33, 34. , 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 47 protruding from the accommodating portion 47 is fitted so that the seal surface 37 on the main valve body 20 side does not separate from the valve seat surface 17 of the upper valve seat 10A. 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. 7 and FIG. 10 (A), 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.

  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 between the ports 12-14 communicated by the second communication path 32, the ports 11-12 communicated by the third communication path 33, and the ports 13-14 communicated by the fourth communication path 33. By rotating the main valve body 20 counterclockwise from the second rotational position by 60 °, between the ports 11-12 communicated by the third communication path 33 and between the ports 13-14 communicated by the fourth communication path The flow path is switched between the ports 11-13 communicating with the first communication path 31 and between the ports 12-14 communicating with the second communication path 32.

  When the flow path switching valve 1 of the present embodiment is incorporated into a heat pump type air conditioning system as shown in FIG. 24, for example, the first port 11 is connected to the compressor discharge side as described above. The high-pressure port D, the second port 12 is 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. 6 (A), 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 into the discharge-side high-pressure port 11 (D) → U-shaped as shown by the white arrow in FIG. 6B (2). The third communication passage 33 → flows to the indoor side inlet / outlet port 12 (E), and the low-pressure refrigerant from the outdoor heat exchanger is connected to the outdoor side inlet / outlet port 13 (C) → the inverted U-shaped fourth communication passage 34 → suction. Flows to the side low pressure port 14 (S).

  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 fitting by the ball-type seal surface isolation mechanism 45, so that switching is performed. 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.

  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.

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

  FIG. 11 shows an example in which the upper half 20A and the lower half 20B of the main valve body 20 of the first embodiment are respectively integrated. That is, in the first 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 joined thereto. In this example, the upper half 20A and the lower half 20B are manufactured as a single unit from the beginning with a 3D printer or the like. Other configurations are the same as those of the first embodiment, and substantially the same effects as those of the first embodiment can be obtained.

  FIG. 12 shows an example in which the upper half 20A and the lower half 20B of the main valve body 20 of the first embodiment are integrated. That is, the whole main valve body 20 (the 1st-4th layer members 21-24) is produced as a one-piece from the beginning with a 3D printer or the like. In this example, since it is impossible to provide means for urging the main valve body 20 in the vertical direction, it is difficult to ensure the required sealing performance.

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

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

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

  FIG. 14A shows (1) the first layer member 21, (2) the second layer member 22, and (3) the third valve member 20 in the state where the main valve body 20 in the second embodiment is in the first rotational position. 3B is a plan view of the third layer member 23, and FIG. 4B is a plan view of the fourth layer member 24. FIG. 5B shows a communication path configuration in a state where the main valve body 20 is in the first rotation position. ) To (4) are cross-sectional views taken along line XX of (A) to (1) to (4).

  FIG. 15A shows (1) the first layer member 21, (2) the second layer member 22, (3) the third layer member 23, in a state where the main valve body 20 is in the second rotational position. 4) Each plan view of the fourth layer member 24, (B) shows the configuration of the communication path in a state where the main valve body 20 is in the second rotational position, (B) (1) upper stage side, lower stage The side is a partial cross-sectional view according to the U-U line of sight and the V-V line of sight in (1) of (A), (B) (2) and (3) are (A) (2) and ( 3) A sectional view according to the YY arrow line, (B) (4) upper side and lower side are respectively the JJ arrow line and the KK arrow line in (4) of (A). FIG.

  When the flow path switching valve 2 of the present embodiment is incorporated into a heat pump type air conditioning system as shown in FIG. 24, unlike the first embodiment, for example, the first port 11 is connected to the compressor discharge side. The discharge side high pressure port D, the second port 12 is connected to the compressor suction side, the suction side low pressure port S, the third port 13 is connected to the outdoor heat exchanger, the outdoor input / output port C, and the fourth port 14 is connected The indoor side input / output port E is connected to the indoor heat exchanger.

  The main valve body 20 of the flow path switching valve 2 of the second embodiment has a first communication path 41 and a first communication path 41 for communicating the first port 11 and the third port 13 when taking the first rotational position. A second communication path 42 that communicates between the 4 port 14 and the second port 12 is provided, and when the second rotation position rotated 90 ° clockwise from the first rotation position is taken, A third communication path 43 that communicates with the fourth port 14 and a fourth communication path 44 that communicates the third port 13 and the second port 12 are provided.

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

  In the first layer member 21 constituting the upper part of the upper half 20A of the main valve body, the two straight through passage portions 41A, spaced apart by 180 °, like the straight through passage portions 21A, 21B of the first embodiment, 41B is provided. Further, as shown in the upper and lower sides of (1) in FIG. 15B, the passage portions 41C and 41D with lateral holes having one end opened (upper surface openings 41a and 41c) and the entire lower surface opened. Provided. The upper surface openings 41a and 41c of the passage portions 41C and 41D with the horizontal holes are arranged at positions 90 ° apart from the straight through-passage portions 41A and 41B, and the lower surface openings other than the other end portions are blocked by the second layer member 22. The other end portions (the lower surface openings 41b and 41d) that are not closed by the second layer member 22 are arranged on a straight line connecting the centers of the straight through passage portions 41A and 41B.

  Therefore, when the main valve body 20 is in the first rotation position, the straight through passage portions 41A and 41B are 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 90 ° clockwise, the upper surface openings of the straight through passage portions 41A and 41B are closed by the upper valve seat 10A, and the upper surface openings of the passage portions 41D and 41C with side holes are the first port 11 and the second port 12. Located directly below.

  The second layer member 22 constituting the lower part of the upper half 20A of the main valve body has four straight lines with a predetermined interval on a straight line connecting the centers of the straight through passage portions 41A and 41B of the first layer member 21 described above. The through passage portions 42A, 42B, 42C, and 42D are provided. The straight through path portions 42 </ b> A and 42 </ b> D are located immediately below the straight through path portions 41 </ b> A and 41 </ b> B of the first layer member 21. The straight through-passage portion 42B is located directly below the lower surface opening 41b of the passage portion 41C with a horizontal hole, and the straight through-passage portion 42C is located directly below the lower surface opening 41d of the passage portion 41D with a horizontal hole.

  The third layer member 23 constituting the upper portion of the lower half 20B of the main valve body has four straight through holes directly below the four straight through passage portions 42A, 42B, 42C and 42D provided in the second layer member 22. Road portions 43A, 43B, 43C, and 43D are provided.

  In the fourth layer member 24 constituting the lower part of the lower half 20B of the main valve body, the two straight through-passage portions 44A, spaced apart by 180 °, like the straight through-passage portions 21A and 21B of the first embodiment, 44B is provided. Further, as shown in FIG. 15B (4) on the upper side and the lower side, the passage portions 44C and 44D with lateral holes having one end opened (lower surface openings 44a and 44c) and the entire upper surface side opened. Provided. The lower surface openings 44a, 44c of the passage portions 44C, 44D with the horizontal holes are disposed at positions 90 ° apart from the straight through-passage portions 41A, 41B, and the upper surface openings other than the other end portions are blocked by the third layer member 23. The other end portions (upper surface openings 44b and 44d) that are not closed by the third layer member 23 are arranged on a straight line connecting the centers of the straight through-passage portions 44A and 44B.

  Therefore, when the main valve body 20 is in the first rotation position, the straight through-passage portions 44A and 44B 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 90 ° clockwise, the lower surface openings of the straight through passage portions 44A, 44B are closed by the lower valve seat 10B, and the lower surface openings 44c, 44a of the lateral hole passage portions 44D, 44C , Located just above the fourth port 14.

  As understood from the above description, when the main valve body 20 takes the first rotational position, the first communication passage 41 that communicates the first port 11 and the third port 13 is the straight through passage portion 41A, 42A, 43A, and 44A, and the 2nd communication path 42 which makes the 4th port 14 and the 2nd port 12 communicate is the straight through passage part 41B, 42D, 43D, and 44B. 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 43 that connects the first port 11 and the fourth port 14 is a passage portion 41D with a horizontal hole in order from the top → a straight through passage portion. It becomes a crank-shaped passage composed of 42C → straight through passage portion 43C → passage portion 44C with a horizontal hole. Further, the fourth communication passage 44 for communicating the third port 13 and the second port 12 is constituted by a passage portion with a horizontal hole 44D → a straight through passage portion 43B → a straight through passage portion 42B → a passage portion with a horizontal hole 41C in order from the bottom. It becomes a crank-shaped passage.

  As described above, in the flow path switching valve 2 of the present embodiment, the main valve body 20 is rotated 90 ° clockwise from the first rotation position, so that the port 11-13 communicates with the first communication path 41. In addition, the flow path is switched from between the ports 14-12 communicated by the second communication path 42 to the ports 11-14 communicated by the third communication path 43 and between the ports 13-12 communicated by the fourth communication path 43. By rotating the main valve body 20 by 90 ° counterclockwise from the second rotation position, between the ports 11-14 communicating by the third communication passage 43 and between the ports 13-12 communicating by the fourth communication passage The flow path is switched between the ports 11-13 communicating with the first communication path 41 and between the ports 14-12 communicating with the second communication path 42.

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

  On the other hand, when performing the heating operation, the main valve body 20 is rotated 90 ° clockwise from the first rotation position to obtain the second rotation position as shown in (1) of FIG. Make it. 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 crank-shaped first as shown by the white arrow in (2) of FIG. The three-way passage 43 → flows to the indoor side inlet / outlet port 14 (E), and the low-pressure refrigerant from the outdoor side heat exchanger enters the outdoor side inlet / outlet port 13 (C) → the crank-like fourth communication passage 44 → the suction side low-pressure port. 12 (S).

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

[Third embodiment of main valve]
FIGS. 16A and 16B show the flow path switching valve of the third embodiment, in which FIG. 16A shows a state where the main valve body is in the first rotational position, and FIG. 16B shows a state where the main valve body is in the second rotational position. Yes, (1) is an upper surface side arrangement view, and (2) is a cross-sectional view taken along the line XX of (1). In FIG. 16, portions corresponding to the respective portions of the flow path switching valve 1 of the first embodiment are denoted by common reference numerals.

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

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

  Even in the flow path switching valve 3 of the present embodiment configured as described above, although there are differences between the three-way switching valve and the four-way switching valve, the same effects as the four-way switching valve 1 of the first embodiment are obtained. It is done.

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

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

  The actuator 7 according to the first embodiment is a fluid pressure type that uses a differential pressure between a high-pressure fluid and a low-pressure fluid that circulates in the main valve 5, and is provided at one end of the lower valve seat 10 </ b> B in the main valve housing 10. It has the main-body part 50 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. 17 shows a state where the pressure receiving moving body 60 is in the lowest lowered position (down movement stroke completion state), and FIG. 18A shows a state where the pressure receiving moving body 60 is in 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 provided between the pressure receiving moving body 60 and the rotation driving body 65 constituting the motion converting mechanism 58. A ball 72, a receiving portion 74 for the ball 72, and a spiral groove 75 are provided to convert the rotational movement into 65 forward and reverse directions.

  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. 19 in addition to FIGS. 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. 17, 18 </ b> A, and FIGS. 21 </ b> A to 21 </ b> D, which will be described later, show states in the middle of rotation of the drive arm 78 and the driven arm 39.

  As shown in FIG. 20, 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).

  FIGS. 17 and 21A show a state in which high pressure fluid (high pressure refrigerant) is introduced into the upper working chamber 55A through the upper port 56 and high pressure fluid is discharged from the lower working chamber 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. 17 and 21A, 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). 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 rotary driving body 65 is also stopped. Hereinafter, this stroke is referred to as an upward movement stroke, and the state shown in FIG. 21B (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. 21C and 21D, in the state where the upward movement stroke is completed, the high pressure fluid is introduced into the working chamber upper portion 55A via the upper port 56, and the working chamber lower portion 55B is lowered to the lower portion. 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 stops and the rotation of the rotation driving body 65 also stops. Hereinafter, this stroke is referred to as a downward movement stroke, and the state shown in FIG. 21D (the state where the pressure receiving moving body 60 is at the lowest 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).

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

  The inside of the valve case portion 81 is a valve chamber 88. 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 its free end side is press-fitted together with the fixture 96 at the end of the plunger 85 opposite to the suction element 84 side.・ It is fixed by caulking. 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, the plunger 85 has its upper end positioned on the valve by the urging force of the compression coil spring 87 as shown in FIG. It is pushed up to a position where it contacts 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 to 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.

  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. 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 + reduction gear.

  The actuator 7 that rotates the main valve body 20 is configured to move the pressure-receiving moving body 60 up and down by fluid pressure, convert this up-and-down movement into a rotational motion, and transmit it to the main valve body 20. The part that receives high pressure compared to the part that is cantilevered by the extension shaft part of the rotating shaft part of the main valve body and has a large pressure receiving area relative to the plate thickness The (pressure receiving moving body 60) can ensure sufficient strength, improve durability, and ensure sufficient strength, so that the pressure receiving area can be increased, and therefore the flow path switching is performed reliably and promptly. be able to.

  In addition to the above, a ball screw mechanism is generally known as a mechanism for converting linear motion to rotational motion. However, the normal ball screw mechanism uses a large number of balls and requires a return structure. Compared to the motion conversion mechanism 58 of the example, the structure is complicated and expensive, and use in a high-temperature and high-pressure environment is not considered. Is difficult. On the other hand, the fluid pressure type actuator provided with the motion conversion mechanism 58 of the present embodiment has an extremely simple configuration with a small number of parts, which is advantageous in terms of cost and measures for use in a high temperature and high pressure environment. (Such as increasing the thickness of the pressure-receiving moving body 60) can be easily achieved. Therefore, the flow path switching valve 1 of the present embodiment is particularly suitable for a flow incorporated in a high-temperature and high-pressure environment such as a heat pump air conditioning system. As a path switching valve, it is extremely cost-effective.

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

  Specifically, the rotary drive body 65 is externally fitted and fixed to the lower rotary shaft portion 30B of the main valve body 20 by press fitting, caulking, etc., so that the rotation of the rotary drive body 65 is directly transmitted to the main valve body 20. It has become. Therefore, in the second embodiment, the rotation transmission mechanism 77 of the actuator 7 is not necessary, and the upward movement of the pressure receiving moving body 60 is stopped by the lower surface 10e of the lower valve seat 10B. The upper surface closing member 53 is also unnecessary. Therefore, the configuration is simplified, which is advantageous in terms of cost.

  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 Seat surface 20 Main valve body 20A Upper half part 20B Lower half 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 rotation shaft portion 30B Lower rotation shaft portion 31 First communication path 32 Second Communication path 33 Third communication path 34 Fourth communication path 36 Protruding portion 37 Seal surface 41 First communication path 42 Second communication path 43 Third communication path 44 Fourth communication path 45 Ball-type seal surface separation mechanism 50 Body (actuator) )
52 Lower surface closing member 53 Upper surface closing 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 Rotating drive body 72 Ball 75 Spiral groove 76 Rotation drive shaft 77 Rotation transmission mechanism 80 Four-way pilot valve 82 Solenoid part 83 Valve seat block 85 Plunger 88 Valve chamber 89 Pore 90 Valve body holder 91 Valve body 92 Valve seat 93 Recesses a, b, c Port (four-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 (17)

A main valve including a main valve housing and a main valve body rotatably disposed in the main valve housing; and a hydraulic actuator for rotating the main valve body, the main valve body comprising: A flow path switching valve configured to be switched by rotating,
The actuator has a main body portion provided with a working chamber into which a high-pressure fluid supplied to the main valve is introduced, and the reciprocating linear motion is forward and backward using the pressure of the high-pressure fluid in the working chamber. A motion conversion mechanism that converts rotational motion in both directions is provided ,
The motion conversion mechanism is configured such that the pressure receiving moving body accommodated in the working chamber so as to be able to move up and down in a state in which the rotation thereof is prevented, and the pressure receiving moving body to be relatively rotatable corresponding to the vertical movement of the pressure receiving moving body. A rotary drive body that is interpolated or extrapolated in the movable body, and in one of the pressure receiving movable body and the rotary drive body, the ball and a part of the ball project in the radial direction. An accommodation portion that is rotatably and accommodated in a state in which movement is substantially prevented, and on the other hand, a part of the ball protruding in a radial direction from the accommodation portion is fitted, and is bent up and down while bending in the circumferential direction. flow path switching valve, wherein the configuration der Rukoto the spiral groove extending direction. On the outer periphery of the pressure-receiving movable body, a packing is installed that hermetically seals between the inner peripheral surface of the working chamber and partitions the working chamber into an upper part and a lower part whose volume is variable. together with the upper port for introducing and discharging a high pressure fluid is provided in the working chamber top to claim 1, characterized in that the lower port for introducing and discharging a high pressure fluid to the lower the working chamber is provided The flow path switching valve described. The actuator introduces a high-pressure fluid into the lower portion of the working chamber via the lower port and discharges the high-pressure fluid from the upper portion of the working chamber via the upper port, thereby moving the pressure-receiving movable body upward. An upward stroke of rotating the rotary drive body in one direction, and introducing high-pressure fluid into the upper portion of the working chamber via the upper port and discharging high-pressure fluid from the lower portion of the working chamber via the lower port. 3. The flow path switching according to claim 2 , wherein the flow switching unit is configured to selectively take a downward movement stroke in which the pressure receiving moving body is moved downward to rotate the rotary drive body in the other direction. valve. Switching between the up stroke and the down stroke is performed by a four-way pilot valve connected to the upper port and the lower port, and a high pressure portion and a low pressure portion in the main valve. The flow path switching valve according to claim 3 . The axis of rotation of the rotary drive member is configured to eccentrically relative to the main valve body axis of rotation, one of claims 1 to 4, characterized in that they are Zaisa distribution parallel to the axis of rotation of the main valve body A flow path switching valve according to claim 1. Wherein one of the rotation of the rotary drive member from claim 1, characterized in that the rotation transmission mechanism is provided for transmitting to the main valve body 5 between the main valve body and the rotary drive member of said actuator The flow path switching valve according to 1. The rotation transmission mechanism is connected and fixed to the drive shaft connected to the drive shaft portion of the rotary drive body, and the rotary shaft portion of the main valve body, and the vicinity of the tip is rotated near the tip of the drive arm. The flow path switching valve according to claim 6 , wherein the flow path switching valve is configured with a driven arm. The rotation transmission mechanism includes a drive gear connected and fixed to a drive shaft portion of the rotation drive body, and a driven gear connected and fixed to the rotation shaft portion of the main valve body and meshing with the drive gear. The flow path switching valve according to claim 6 . The drive shaft portion of the rotation drive body and the rotation shaft portion of the main valve body are arranged on a common axis so that the main valve body and the rotation drive body rotate integrally. The flow path switching valve according to any one of claims 1 to 4 , wherein The main valve housing has a cylindrical shape in which an upper surface opening and a lower surface opening are hermetically sealed by an upper valve seat and a lower valve seat, and at least a total of the upper valve seat and / or the lower valve seat Three ports are provided, and a plurality of communication passages for selectively communicating between the ports are provided in the main valve body rotatably disposed in the main valve housing, and the actuator wherein by rotating the main valve body, the flow path switching valve according to claim 1, characterized in that it is adapted between port communicating is switched 9 by. At least one first communication passage capable of communicating at least one of the ports with another one and at least one of the ports and another one within the main valve body. A second communication path is provided, and by switching the main valve body in one direction, the flow path can be switched from the port communicating with the first communication path to the port communicating with the second communication path. The flow path is switched between the ports communicating with the second communication path and the ports communicating with the first communication path by rotating the main valve body in the other direction after the flow path switching. The flow path switching valve according to claim 10 , wherein the flow path switching valve is configured as described above. First, second, third and fourth ports are provided in the upper valve seat and / or the lower valve seat,
When the main valve body is in the first rotation position, the first communication passage for communicating the first port and the third port and the second port and the fourth port are communicated with the main valve body. Two passages,
When the main valve body is in the second rotational position, the third communication path that communicates the first port with the second port or the fourth port and the third port communicates with the fourth port or the second port. The flow path switching valve according to claim 10 or 11 , wherein a fourth communication path is provided. The flow path switching valve according to claim 12 , wherein the upper valve seat is provided with first and second ports, and the lower valve seat is provided with third and fourth ports. The flow path switching valve according to any one of claims 10 to 13 , wherein at least one of the plurality of communication paths is constituted by a linear path as a whole. The flow path switching valve according to any one of claims 10 to 14 , wherein at least one of the plurality of communication paths is configured as a U-shaped or crank-shaped path. The convex portion having an annular sealing surface that is in close contact with the periphery of the opening of each port in the upper valve seat and / or the lower valve seat is protruded from both ends of the communication passage. The flow path switching valve according to any one of 10 to 15 . 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. The flow path switching valve according to any one of claims 10 to 16 , wherein a biasing means for biasing is interposed.

Images