JP2006349274A - Throttle device, flow control valve and air conditioner incorporating them - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve the problem of high costs of parts of conventional flow control valves that incorporate porous members in order to subdivide air bubbles contained in fluid. <P>SOLUTION: The flow control valve includes a valve housing 26 formed with a valve chamber 25; a first opening 27 facing the valve chamber 25; a second opening 29 formed with a valve seat 28 facing the valve chamber 25; a valve element 30 caused to abut against the valve seat 28 and movably held in such a manner as to close the second opening 29; and a drive means connected to the valve housing 26 for driving the valve element 30. The valve element 30 has an inner gap part 50 being cylindrical about the axis of the valve element and being in communication with the second opening 29 at one end along the axis; a cylindrical outer gap part 51 concentrically surrounding the inner gap part 50; a port 52 extending radially outward from the outer gap part 50 and being open to the valve chamber 25; and a throttle passage 53 disposed 180 degrees away from the port 52 and communicating the inner gap part 50 with the outer gap part 51. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a throttling device, a flow control valve having the same throttling function, and an air conditioner in which the flow control valve is incorporated in a refrigerant circulation passage.

  In an air conditioner having a dehumidifying function, the upstream indoor heat exchanger functions as a condenser and the downstream indoor heat exchanger functions as an evaporator during a dehumidifying operation using a pair of indoor heat exchangers. What was made known is known. When performing a dehumidifying operation with such an air conditioner, the indoor air is heated by the upstream heat exchanger, while the indoor air is cooled and dehumidified by the downstream heat exchanger, thereby reducing the indoor air temperature. Consideration can be given to dehumidification without lowering. In the air conditioner incorporating this pair of indoor heat exchangers, a flow control valve having a throttling function is assembled in the refrigerant passage connecting the upstream indoor heat exchanger and the downstream heat exchanger, and dehumidifying operation is performed. When performing the above, it is necessary to keep the refrigerant passage in a narrowed state.

  When dehumidifying operation is performed, a liquid phase and a gas phase refrigerant are mixed in the refrigerant passage on the upstream side of the flow control valve, and the pressure suddenly changes when the gas phase refrigerant passes through the throttle. As a result, annoying noise is generated. For example, Patent Literature 1 and Patent Literature 2 disclose techniques for reducing such noise. In Patent Document 1, a porous permeable material is incorporated on the outlet side of the throttle portion so as to subdivide by suppressing explosive expansion of bubbles. In Patent Document 2, a plurality of orifices are overlapped with each other through a space, and noise generated when passing through the orifice is buffered in the space so as to be silenced.

JP 2003-202167 A JP 2003-065632 A

  In the case of the conventional flow control valve disclosed in Patent Document 1, in order to obtain a predetermined silent effect, it is necessary to set the thickness of the porous permeable material along the refrigerant flow direction to a certain degree. For this reason, in a flow control valve in which the inlet port and the outlet port are orthogonal to each other and a porous permeable material is incorporated in the valve body that opens and closes the outlet port side, the refrigerant is throttled while the outlet port side is closed by the valve body. Therefore, the refrigerant flow path in the flow control valve must be bent greatly from the inlet port to the opposite side of the outlet port, resulting in pressure loss or an increase in the size of the flow control valve itself. End up. In addition, since the material cost of the porous permeation material increases, it also contributes to increase the cost of the flow control valve itself.

  Further, in the decompression device disclosed in Patent Document 2, it is necessary to arrange a plurality of orifices and a space in series along the flow direction of the refrigerant, and in order to obtain a sufficient silent effect, a large volume is required. Therefore, there is a disadvantage that the size of the decompression device is increased. In addition, in this decompression device, it is basically impossible to reduce the noise generated when the refrigerant passes through the downstream orifice of the last stage.

  An object of the present invention is to provide a throttle device that can obtain a low noise effect at low cost, a flow control valve incorporating the throttle device, and an air conditioner incorporating the flow control valve.

  The first embodiment of the present invention has a cylindrical shape, and an inner space portion whose one end side along the axis communicates with the outside, and an outer space having a cylindrical shape formed so as to concentrically surround the inner space portion. And a port extending radially outward from the outer gap and communicating with the outer gap, and spaced apart from the port by 180 degrees to communicate the inner gap and the outer gap. A throttling device comprising a throttling passage.

  In the present invention, when a fluid is introduced from the port into the outer gap, the fluid is guided to the inner gap through the throttle passage separated by 180 degrees, and the fluid flows out from one end side of the inner gap. . Conversely, when fluid is introduced from one end side of the inner gap portion into the inner gap portion, the fluid is guided to the outer gap portion through the throttle passage, and further from the port located 180 degrees opposite to the throttle passage. Leaks. In any case, the flow velocity of the fluid and the pressure decrease due to the throttling effect when passing through the throttling passage. When the fluid is introduced from the port into the outer gap, the fluid flow rate gradually decreases immediately after passing through the throttle passage, and the reduced pressure stabilizes in the inner gap. On the other hand, when the fluid is introduced from one end side of the inner gap to the inner gap, the flow rate of the fluid immediately after passing through the throttle passage gradually decreases and the reduced pressure stabilizes. Will happen.

  In the throttling device according to the first aspect of the present invention, it is preferable that the thickness along the radial direction of at least one of the inner gap and the outer gap is set smaller than the inner diameter of the throttling passage.

  The diaphragm device may further include a filter that covers the port.

  A second port that communicates between the outside and one end of the inner space can further be provided, and the second port can be arranged symmetrically with respect to the axis of the inner space. In this case, a plurality of second ports may be opened radially from one end side of the inner space to the radially outer side.

  According to a second aspect of the present invention, a valve housing having a valve chamber formed therein, a first opening extending in a first direction and facing the valve chamber of the valve housing, and the first direction A second opening in which a valve seat extending in the second direction so as to cross the valve chamber and facing the valve chamber of the valve housing is formed, and the valve seat of the second opening abuts on the second seat A valve body movably held in the second direction so as to close the two openings, and a driving means connected to the valve housing for driving the valve body in the second direction. The valve body has a cylindrical shape centering on an axis parallel to the second direction, and an inner gap portion whose one end side along the axis communicates with the second opening, and an inner side thereof A cylindrical outer cavity formed concentrically surrounding the cavity, and extending radially outward from the outer cavity A flow control valve having a port that opens to the valve chamber side, and a throttle passage that is disposed 180 degrees apart from the port and communicates the inner gap and the outer gap. .

  In the present invention, when the fluid is introduced from the port into the outer gap, the fluid is guided from the throttle passage separated by 180 degrees to the inner gap, and the fluid flows out from one end side of the inner gap. Conversely, when fluid is introduced from one end side of the inner gap portion into the inner gap portion, the fluid is guided to the outer gap portion via the throttle passage, and further, the fluid flows out from the port located on the opposite side of the throttle passage. To do. In any case, the flow velocity of the fluid and the pressure decrease due to the throttling effect when passing through the throttling passage. When the fluid is introduced from the port into the outer gap, the flow velocity of the fluid immediately after passing through the throttle passage and the pressure stabilization gradually occur in the inner gap. On the other hand, when the fluid is introduced from the one end side of the inner gap to the inner gap, the flow velocity of the fluid immediately after passing through the throttle passage gradually decreases and the reduced pressure is stabilized.

  In the flow control valve according to the second aspect of the present invention, the thickness along the radial direction of at least one of the inner gap portion and the outer gap portion along the radial direction of the valve body may be set smaller than the inner diameter of the throttle passage. preferable.

  The flow control valve can further include a cylindrical filter covering the port.

  In a state in which the valve body is in contact with the valve seat of the second opening, the port can be positioned in the extending region along the first direction of the fluid passage defined by the first opening. .

  A second port communicating with the second opening and the one end side of the inner space can further be provided, and the second port can be arranged axisymmetrically with respect to the axis of the inner space. In this case, a plurality of second ports may be opened radially from one end side of the inner space to the outer side in the radial direction.

  In a state where the valve body is in contact with the valve seat of the second opening, it is preferable that one end side of the inner gap portion is opened close to the inner wall of the valve seat of the second opening.

  The third aspect of the present invention includes a compressor, an outdoor heat exchanger, a pair of indoor heat exchangers, a refrigerant circulation passage that sequentially passes through the compressor, the outdoor heat exchanger, and the pair of indoor heat exchangers. And a flow control valve according to a second embodiment of the present invention incorporated in a circulation passage connecting the pair of indoor heat exchangers, wherein the first opening of the flow control valve continues to the outdoor heat exchanger. The air conditioner is characterized in that it is connected to the indoor heat exchanger side and the second opening is connected to the other indoor heat exchanger side following the compressor.

  In the present invention, the flow control valve is open during normal cooling operation, and the refrigerant compressed by the compressor is the outdoor heat exchanger, one indoor heat exchanger, the flow control valve, and the other indoor heat exchanger. Then, it returns to the compressor again, and the room is cooled by a pair of indoor heat exchangers. In contrast, during the dehumidifying operation, the flow control valve is in a closed state, the refrigerant flow from one indoor heat exchanger to the other indoor heat exchanger is suppressed, and a pair of moisture present in the room is removed. This is deposited on the indoor heat exchanger and discharged outside the room.

  According to the throttle device of the present invention, an inner cavity that is cylindrical and has one end along the axis communicating with the outside, and a cylindrical outer cavity formed so as to concentrically surround the inner cavity. And a port that extends radially outward from the outer space and communicates with the outer space, and a throttle passage that is disposed 180 degrees away from the port and communicates the inner space and the outer space. Therefore, when fluid flows from the outer gap to the inner gap via the throttle passage, the fluid flow rate increases and the pressure decreases due to the throttle effect when passing through the throttle passage. A decrease in fluid flow rate and pressure stabilization immediately after passing through the throttle passage will gradually occur in the inner gap. As a result, even in the case of using a particularly easily vaporized fluid, the expansion sound accompanying vaporization does not occur instantaneously immediately after passing through the passage, and the inside void after passing through the throttle passage is sequentially generated during the flow. It can be made quieter than those. Conversely, when fluid flows from one end of the inner cavity to the inner cavity via the throttle passage, the fluid is gradually increased in the outer cavity and the pressure is stabilized and the port is stabilized. Can lead. Moreover, it is not necessary to use an expensive porous member for noise reduction, and it is possible to suppress the component cost and the manufacturing cost.

  When the thickness along the radial direction of the outer gap is set smaller than the inner diameter of the throttle passage, bubbles contained in the fluid are subdivided from the inner diameter of the passage when the fluid flows into the throttle passage from the outer gap. It is possible to reduce the width of the pressure fluctuation generated when the bubbles pass through the throttle passage. On the contrary, when the fluid flows into the outer gap through the throttle passage, the flow velocity of the fluid raised by the throttling effect in the throttle passage can be lowered slowly and the lowered pressure can be stabilized.

  Similarly, when the thickness along the radial direction of the inner gap is set smaller than the inner diameter of the throttle passage, when the fluid flows into the inner gap through the throttle passage, it increases due to the throttle effect in the throttle passage. The flow rate of the fluid can be lowered slowly and the reduced pressure can be stabilized. On the contrary, when the fluid flows into the throttle passage from the inner gap, the bubbles contained in the fluid can be subdivided from the inner diameter of the passage, and the width of the pressure fluctuation generated when the bubbles pass through the throttle passage Can be reduced.

  According to the flow control valve of the present invention, the valve housing formed with the valve chamber, the first opening facing the valve chamber of the valve housing, and the second opening formed with the valve seat facing the valve chamber of the valve housing. And a valve body movably held so as to abut against the valve seat of the second opening and close the valve seat, the valve body having a cylindrical shape centered on the axis thereof, And an inner cavity whose one end along the axis communicates with the second opening, a cylindrical outer cavity formed so as to concentrically surround the inner cavity, and a diameter from the outer cavity. A throttle passage that extends outward in the direction and opens to the valve chamber side, and a throttle passage that is disposed 180 degrees away from the port and communicates the inner gap portion and the outer gap portion. A state in which the first opening and the second opening are communicated with each other without using A first opening and a second opening can be switched between a state of communicated. In addition, when the first and second openings communicate with each other through the throttle passage, the flow velocity of the fluid increases and the pressure decreases when passing through the throttle passage. As the flow rate gradually decreases, the pressure stabilizes in the inner or outer gap. As a result, even when using a fluid that is particularly easy to vaporize, an expansion sound accompanying vaporization does not instantaneously occur immediately after passing through the throttle passage, and the inside or outside gap after passing through the throttle passage is sequentially flowing. Therefore, the noise can be reduced without using an expensive porous member for noise reduction. In addition, it is not necessary to use a porous member for noise reduction, and it is possible to suppress the component cost and the manufacturing cost.

  When the thickness of the outer gap along the radial direction of the valve body is set to be smaller than the inner diameter of the throttle passage, when the fluid flows into the throttle passage from the outer gap, bubbles contained in the fluid are removed from the inner diameter of the throttle passage. Can be subdivided, and the width of the pressure fluctuation generated when the bubbles pass through the throttle passage can be reduced. Conversely, when the fluid flows into the outer gap through the throttle passage, the flow rate of the fluid raised by the throttle passage can be lowered slowly and the reduced pressure can be stabilized.

  Similarly, when the thickness of the inner gap along the radial direction of the valve body is set smaller than the inner diameter of the throttle passage, the fluid that has risen by the throttle passage when the fluid flows into the inner gap through the throttle passage The flow rate of the gas can be slowly reduced and the reduced pressure can be stabilized. Conversely, when the fluid flows into the throttle passage from the inner gap, the bubbles contained in the fluid can be subdivided from the inner diameter of the throttle passage, and pressure fluctuations that occur when the bubbles pass through the throttle passage can be reduced. The width can be reduced.

  In a state where the valve body is in contact with the valve seat of the second opening, when the port is positioned in the extending region along the first direction of the fluid passage defined by the first opening, the port And the fluid passage formed by the first opening, the fluid smoothly flows along the first direction, and noise generated with a change in the fluid flow direction can be eliminated.

  In a state where the valve body is in contact with the valve seat of the second opening, when one end side of the inner gap is opened close to the inner wall of the valve seat of the second opening, the fluid is in the inner gap. When flowing out from the one end side to the second opening side, it becomes possible to flow the fluid along the inner wall of the valve seat of the second opening, and the two phases of the liquid on the inner peripheral side and the gas on the outer peripheral side Mixing of fluids that are easy to separate can be contemplated.

  According to the air conditioner of the present invention, one indoor heat in which the first opening of the flow control valve according to the second embodiment of the present invention incorporated in the circulation passage connecting the pair of indoor heat exchangers follows the outdoor heat exchanger. Since it is connected to the exchanger side and the second opening is connected to the other indoor heat exchanger side following the compressor, the passage sound of the refrigerant passing through the flow rate control valve during dehumidifying operation can be easily and It can be reduced with an inexpensive configuration.

  Embodiments in which the flow control valve according to the present invention is applied as a throttle valve for dehumidification of an air conditioner will be described in detail with reference to FIGS. 1 to 5, but the present invention is not limited to these embodiments. Can be combined, or any change or modification included in the concept of the present invention described in the claims can be applied, so that it can be applied to any other technology belonging to the spirit of the present invention. it can.

  The concept of the air conditioner in this embodiment is shown in FIG. That is, the air conditioning apparatus 10 in this embodiment includes a compressor 11 that compresses a gas-phase refrigerant to a high pressure, and a 4-port 2-position switching that communicates with the compressor 11 via a refrigerant supply pipe 12 and a refrigerant return pipe 13. A valve (hereinafter referred to as a directional control valve) 14, an outdoor heat exchanger 16 communicating with the directional control valve 14 via a refrigerant circulation pipe 15, and a refrigerant circulation pipe 17 connected to the outdoor heat exchanger 16. A first indoor heat exchanger 18 that communicates, an expansion valve 19 incorporated in the refrigerant circulation pipe 17 that connects the first indoor heat exchanger 18 and the outdoor heat exchanger 16, and a first indoor heat A second indoor heat exchanger 22, a first indoor heat exchanger 18, and a second indoor heat exchanger that communicate with the exchanger 18 and the previous direction control valve 14 via refrigerant circulation pipes 20 and 21, respectively. The refrigerant circulation pipe 20 connecting the And a dehumidifying throttle valve 23 as a flow rate control valve of the present invention incorporated in the above, and a blower fan 24 for guiding the indoor air to the pair of indoor heat exchangers 18 and 22 and sending them out into the room again. . Further, based on a detection signal from a temperature sensor (not shown) and a command from an operation switch, the compressor 11, the direction control valve 14, the outdoor heat exchanger 16, a pair of indoor heat exchangers 18, 22, an expansion valve 19, and a dehumidifier. A control device (not shown) for controlling the operation of the throttle valve 23 is also provided.

  The direction control valve 14 is for switching the circulating flow direction of the refrigerant between the cooling operation and the heating operation. For this reason, the cooling operation position where the refrigerant supply pipe 12 is communicated with the refrigerant circulation pipe 15 connected to the outdoor heat exchanger 16 and the refrigerant return pipe 13 is communicated with the refrigerant circulation pipe 21 connected with the second indoor heat exchanger 22. And a heating operation position where the refrigerant supply pipe 12 communicates with the refrigerant circulation pipe 21 connected to the second indoor heat exchanger 22 and the refrigerant return pipe 13 communicates with the refrigerant circulation pipe 15 connected with the outdoor heat exchanger 16; Can be switched to.

  The expansion valve 19 has a variable valve opening position for adiabatically expanding to a low temperature and low pressure state without causing a phase change of the refrigerant passing therethrough during the cooling / heating operation, and does not act on the refrigerant during the dehumidifying operation. And a valve-opening position for simply passing it through.

  The dehumidifying throttle valve 23 has an open position that does not restrict the flow of refrigerant between the pair of indoor heat exchangers 18 and 22 during the cooling and heating operation, and the first indoor heat exchanger 18 and the second indoor heat exchanger 18 during the dehumidifying operation. It is possible to switch to a valve closing position that restricts the flow of refrigerant to and from the heat exchanger 22.

  In the normal cooling operation mode, the dehumidifying throttle valve 23 is in the open position, and in FIG. 1, the refrigerant circulates in the direction of the arrow and passes through the pair of indoor heat exchangers 18 and 22. Heat exchange is performed between the room and the room.

  In the cooling and dehumidifying operation mode, the expansion valve 19 is switched to the open position and the dehumidifying throttle valve 23 is switched to the closed position while the direction control valve 14 is in the cooling operation position. 1, the refrigerant circulates in the direction of the arrow. In this case, since the expansion valve 19 is in the open position, the relatively high-temperature and high-pressure refrigerant that has passed through the outdoor heat exchanger 16 is directly introduced to the first indoor heat exchanger 18, and this first indoor heat exchange is performed. Heat exchange is performed between the vessel 18 and the room air to cause heating of the room air. On the other hand, since the low-temperature and low-pressure refrigerant is guided to the second indoor heat exchanger 22 located on the downstream side of the dehumidifying throttle valve 23 in the closed state, the second indoor heat exchanger 22 and The indoor air that is heat-exchanged between the two is cooled. Accordingly, the indoor air is dehumidified by the second indoor heat exchanger 22, and the indoor air is heated by the first indoor heat exchanger 18, thereby preventing a decrease in the indoor air temperature during the dehumidifying operation.

  In the heating operation mode, the dehumidifying throttle valve 23 is in the open position, and the refrigerant circulates in the direction opposite to the arrow direction in FIG. 1 except for the refrigerant flow in the refrigerant supply pipe 12 and the refrigerant return pipe 13. The heat exchange is performed between the high-temperature and high-pressure refrigerant passing through the indoor heat exchangers 18 and 22 and the room air.

  A sectional structure of the dehumidifying throttle valve 23 in this embodiment is shown in FIG. 2 in an open state, and its main part is extracted and enlarged and shown in a closed state in FIG. 4 shows. That is, the dehumidifying throttle valve 23 in the present embodiment is a so-called normally open electromagnetic drive type that is opened when no power is supplied, and includes a valve housing 26 having a valve chamber 25 formed therein, A first opening 27 extending in one direction (left-right direction in FIG. 2) and facing the valve chamber 25 of the valve housing 26, and a second direction (FIG. 2) crossing the first direction. And a second opening 29 formed with a valve seat 28 facing the valve chamber 25 of the valve housing 26, and the valve seat 28 of the second opening 29 in contact with the second seat 29. A valve body 30 held so as to be movable in the second direction so as to close the second opening 29, and a driving means 31 connected to the valve housing 26 to drive the valve body 30 in the second direction; It has. In the valve opening position shown in FIG. 2 in which the valve body 30 is separated from the valve seat 28, the first opening 27 and the second opening 29 are in communication with each other via the valve chamber 25 of the valve housing 26. On the contrary, in the valve closing position shown in FIG. 3 where the valve body 30 presses against the valve seat 28, the first opening 27 and the second opening 29 are the throttle device described later incorporated in the valve body 30. Communicate via

  Refrigerant circulation pipes 20 communicating with the pair of indoor heat exchangers 18 and 22 are connected to the first and second openings 27 and 29 of the valve housing 26 via pipe joints 32 and 33, respectively. The opening 27 communicates with the first indoor heat exchanger 18 side, and the second opening 29 communicates with the second indoor heat exchanger 22 side. A base end portion of a guide tube 34 extending in the second direction is joined to the opposite side of the second opening 29 across the valve chamber 25 of the valve housing 26. A cylindrical collar 36 surrounding the base portion of the valve portion 35 formed at the distal end portion of the valve body 30 in the valve open state is accommodated inside. The collar 36 is in a state of being locked to an inner flange 37 formed in the valve housing 26, and a tip portion thereof faces the valve chamber 25. A plug 38 that closes the inside of the guide tube 34 is tightly fitted at the end of the guide tube 34 that protrudes from the valve housing 26 in the direction opposite to the second pipe joint 33.

  The valve body 30 accommodates a plunger 39 having a cup-shaped cross section that is slidably received in the guide tube 34 and into which the tip of the plug 38 can penetrate, and an annular buffer member 40 that can contact the tip of the plug 38. The base end is caulked integrally with the bottom of the plunger 39, the valve stem 41 is formed with the valve portion 35 at the tip, and the valve portion 35 of the valve stem 41 is formed on the second opening 29 side. A recess 43 having a stepped portion 42 that opens toward the top, a bush 44 accommodated in the recess 43, and a cylindrical throttle tube 45. The bush 44 includes a flange portion 46 that abuts against the bottom surface of the recess 43, and a core portion 47 having a smaller diameter than the flange portion 46. Further, the throttle cylinder 45 is locked to a partition wall portion 48 whose tip abuts against the flange portion 46 of the bush 44 and a step portion 42 formed at the base end of the partition wall portion 48 and formed on the inner periphery of the recess 43. And a flange portion 49. The bush 44 and the throttle cylinder 45 obtained from metal or resin or the like have a distal end of the valve portion 35 of the valve stem 41 whose outer periphery is tapered toward the second opening 29 side, that is, an opening of the recess 43. The end is caulked to the inner peripheral side to be held in the recess 43.

  The partition wall portion 48 of the throttle tube 45 defines a cylindrical inner space portion 50 between the outer peripheral surface of the core portion 47 of the bush 44 and an outer space portion 51 between the inner peripheral surface of the recess portion 43. Define. In the present embodiment, a step portion 42 having an inner diameter larger than the outer diameter of the flange portion 46 of the bush 44 is formed on the opening end side of the concave portion 43, and the flange portion 49 of the throttle tube 45 is fitted to the step portion 42. Thus, two gaps 50 and 51 are simultaneously formed between the bush 44 and the recess 43. A first port 52 that connects the first opening 27 and the outer gap 51 is formed in the concave portion 43 of the valve stem 41. In addition, a throttle passage 53 that connects the outer gap 51 and the inner gap 50 is formed in the partition wall 48 of the throttle cylinder 45 located on the opposite side of the first port 52. The front and rear of the aperture stop device in the present embodiment constitute the diaphragm device. An opening end 54 forming an annular shape of the inner gap 50 facing the second opening 29 side functions as a port (hereinafter referred to as a second port for convenience) during closing of the dehumidifying throttle valve 23. .

  The thickness along the radial direction of the inner gap 50, that is, the distance between the outer peripheral surface of the core portion 47 of the bush 44 and the inner peripheral surface of the partition wall portion 48 of the throttle cylinder 45 is set to be narrower than the inner diameter of the throttle passage 53. ing. Similarly, the thickness of the outer space 51 along the radial direction, that is, the distance between the outer peripheral surface of the partition wall 48 of the throttle cylinder 45 and the inner peripheral surface of the recess 43 is also set narrower than the inner diameter of the throttle passage 53. In general, it is generally preferable that the thickness of the gaps 50 and 51 along the radial direction is set to be narrow to about ¼ of the inner diameter of the throttle passage 53 because the throttle passage 53 and the inner and outer gaps are narrow. This is because the change in the cross-sectional area of the flow path between the portions 50 and 51 is the smoothest. From the viewpoint of noise reduction, it can be said that it is preferable to set these intervals as narrow as possible. Since the two gaps 50 and 51 communicating with both sides of the throttle passage 53 define a slit-like refrigerant passage extending in a direction orthogonal to the axis of the throttle passage 53, noise generated in the throttle passage 53 However, it is difficult to be transmitted from the two gaps 50 and 51 to the outside, and good silence can be obtained.

  By the way, if a minute foreign matter or the like is mixed in the refrigerant in the refrigerant circulation passage 20, such a foreign matter blocks the throttle passage 53 formed in the throttle cylinder 45, and the dehumidifying throttle valve 23 is normal. There is a possibility that the function cannot be performed. In order to avoid such a problem, it is preferable to provide a filter formed of a porous member or the like for capturing foreign matter on the upstream side of the expansion device. From such a viewpoint, a cylindrical filter 55 formed of a metal mesh so as to come into contact with the base end surface of the valve portion 35 is fitted on the base portion side of the valve portion 35 of the valve rod 41. The other end surface of the filter 55 is detachably fitted to the outer periphery of the valve stem 41 using a spring force so that the inner peripheral surface side of the filter 55 can completely cover the first port 52 with a gap. The snap ring 56 is integrally fixed to the valve portion 35.

  In the present embodiment, the outer peripheral side of the first port 52 is in the closed position as shown in FIG. 3 where the conical outer peripheral surface of the valve portion 35 of the valve rod 41 contacts the valve seat 28 of the second opening 29. Are set so as to be located in the extending region Z along the first direction of the refrigerant passage defined by the first opening 27, so that the first port 52 and the first opening The flow direction of the fluid flowing between the portions 27 can be maintained substantially linear without being strongly bent, and noise can be reduced by this.

  The driving means 31 of the valve body 30 in the present embodiment uses an electromagnetic coil 57, and a bobbin 58 that accommodates the electromagnetic coil 57, and the bobbin 58 is embedded together with the electromagnetic coil 57 via a sealing resin 59. And a frame-like casing 61 fixed to the plug 38 via a bolt 60. A cable 62 drawn out from the electromagnetic coil 57 through the sealing resin 59 is connected to a power source through an unillustrated on / off circuit. The bobbin 58 is disposed so as to surround the plunger 39 via the guide cylinder 34, and generates an electromagnetic force that moves the plunger 39 toward the valve housing 26 when energized.

  A compression coil spring 63 that urges the valve body 30 away from the valve seat 28 is incorporated in the guide tube 34 between the collar 36 and the bottom of the plunger 39. Sometimes, the first opening 27 and the second opening 29 are in communication with each other via the valve chamber 25 of the valve housing 26 without the valve body 30.

  As described above, the electromagnetic coil 57 is conducted during the dehumidifying operation, the valve body 30 is urged toward the second opening 29 against the spring force of the compression coil spring 63, and the valve portion 35 is moved to the valve seat 28. Is brought into a closed state as shown in FIG. Accordingly, the gas-liquid two-phase refrigerant flowing from the first opening 27 into the valve chamber 25 of the valve housing 26 flows through the filter 55 from the first port 52 into the outer gap 51. Is compressed gradually as it flows along the outer peripheral surface of the partition wall 48 of the throttle cylinder 45 toward the throttle passage 53 on the opposite side by 180 degrees, and large bubbles are subdivided and flow into the throttle passage 53. Here, the refrigerant is further compressed, and the refrigerant having a predetermined flow rate is guided to the second opening 29 side. The refrigerant guided from the throttle passage 53 to the inner gap portion 50 spreads radially along the outer peripheral surface of the core portion 47 of the bush 44, but since the inner gap portion 50 is thin, its rapid expansion is suppressed and the refrigerant is loose. It flows out to the second opening 29 from the second port 54 that is the opening end. As a result, noise generated with the expansion of the bubbles can be suppressed to a low level.

  Note that, in a flow path in which two phases of gas and liquid are mixed, there is a possibility that bubbles are fixed to the inner wall of the flow path and the cross-sectional area of the flow path is substantially narrowed, thereby impairing the smooth flow of refrigerant. In the embodiment, since the opening end of the second port 54 facing the second opening 29 side is opened close to the inner wall of the second opening 29, the second port 54 extends to the second opening 29. The refrigerant that flows out brings about the effect of causing the bubbles attached to the inner wall of the second opening 29 to flow.

  In the above-described embodiment, the flow control valve of the present invention is used as the dehumidifying throttle valve 23, but it can also be applied to the expansion valve 19 and is particularly useful as a refrigerant passage throttle device in a refrigeration cycle.

  In the embodiment described above, the opening end 54 of the inner gap 50 is used as it is as the second port facing the second opening 29, but it can also be opened toward the inner peripheral surface of the second opening 29. FIG. 5 shows a cross-sectional structure of the main part of another embodiment of the flow control valve according to the present invention. However, the same reference numerals are used for elements having the same functions as those of the previous embodiment, The overlapping description will be omitted. That is, in this embodiment, the throttle cylinder 45 has a bottom with a cup-shaped cross section, and the flange portion 49 is formed in the step of the recess 43 in a state where the core portion 47 of the bush 44 is accommodated in the partition wall portion 48 of the throttle cylinder 45. These are fixed integrally by fitting to the part 42 and caulking the tip of the valve part 35 inward. A plurality of second ports 54 are formed radially at the proximal end portion of the partition wall portion 48 of the throttle tube 45 protruding from the distal end of the valve portion 35, and communicate with the inner gap portion 50 and the second opening portion 29. ing. In this way, by opening the plurality of second ports 54 toward the inner wall of the second opening 29 at the base end portion of the partition wall portion 48 of the throttle tube 45, the refrigerant flowing out of the second port 54 is opened to the second opening. It blows out toward the inner wall of the part 29, and the bubbles adhering to the second opening 29 can be more efficiently separated.

  Also in the present embodiment, the refrigerant flows in a semicircular arc shape from the first port 52 along the outer peripheral surface of the partition wall portion 48 of the throttle cylinder 45, passes through the throttle passage 53, and then passes through the bush 44 in the inner gap portion 50 again. It flows along the outer peripheral surface of the core portion 47 and finally flows out from the second port 54 along the inner wall of the second opening 29. Needless to say, the filter 55 contributes to the rectification effect of the refrigerant in addition to capturing foreign matter.

It is a conceptual diagram of one Embodiment of the air conditioning apparatus by this invention. It is sectional drawing showing the schematic structure of one Embodiment of the flow control valve integrated as a throttle valve for dehumidification in the air conditioning apparatus shown in FIG. FIG. 3 is an extracted enlarged cross-sectional view of a main part of the dehumidifying throttle valve shown in FIG. 2. FIG. 4 is a cross-sectional view taken along arrow IV-IV in FIG. 3. It is sectional drawing showing the schematic structure of other embodiment of the flow control valve by this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Air conditioning apparatus 11 Compressor 12 Refrigerant supply pipe 13 Refrigerant return pipe 14 Direction control valve (4 port 2 position switching valve)
DESCRIPTION OF SYMBOLS 15 Refrigerant circulation piping 16 Outdoor heat exchanger 17 Refrigerant circulation piping 18 1st indoor heat exchanger 19 Expansion valve 20, 21 Refrigerant circulation piping 22 2nd indoor heat exchanger 23 Dehumidification throttle valve 24 Blower fan 25 Valve chamber 26 Valve housing 27 First opening 28 Valve seat 29 Second opening 30 Valve body 31 Driving means 32, 33 Pipe joint 34 Guide tube 35 Valve portion 36 Collar 37 Inner flange 38 Plug 39 Plunger 40 Buffer member 41 Valve rod 42 Stepped portion 43 Recessed portion 44 Bushing 45 Blowing tube 46 Flange portion 47 Core portion 48 Partition wall portion 49 Flange portion 50 Inner gap portion 51 Outer gap portion 52 First port 53 Throttle passage 54 Open end of the inner gap portion (second port)
55 Filter 56 Snap Ring 57 Electromagnetic Coil 58 Bobbin 59 Sealing Resin 60 Bolt 61 Casing 62 Cable 63 Compression Coil Spring Z Extension region of the refrigerant passage defined by the first opening along the first direction

Claims (7)

An inner cavity that is cylindrical and has one end along the axis communicating with the outside;
A cylindrical outer cavity formed concentrically surrounding the inner cavity,
A port extending radially outward from the outer gap, and communicating with the outer gap,
A throttling device comprising: a throttling passage arranged 180 degrees apart from the port and communicating the inner gap and the outer gap.   2. The diaphragm device according to claim 1, wherein a thickness of at least one of the inner gap section and the outer gap section along a radial direction is set smaller than an inner diameter of the throttle passage. A valve housing having a valve chamber formed therein; a first opening extending in the first direction and facing the valve chamber of the valve housing; and a second direction intersecting the first direction A second opening formed with a valve seat extending toward the valve chamber of the valve housing and contacting the valve seat of the second opening to close the second opening A valve body held movably in the second direction, and a driving means connected to the valve housing for driving the valve body in the second direction,
An inner void portion having a cylindrical shape centering on an axis parallel to the second direction and having one end side along the axis communicating with the second opening;
A cylindrical outer cavity formed concentrically surrounding the inner cavity,
A port extending radially outward from the outer gap and opening to the valve chamber side,
A flow control valve characterized by having a throttle passage that is arranged 180 degrees apart from the port and communicates the inner gap and the outer gap.   The flow control valve according to claim 3, wherein a thickness of at least one of the inner gap and the outer gap along the radial direction of the valve body is set smaller than an inner diameter of the throttle passage.   In a state where the valve body is in contact with the valve seat of the second opening, the port is located in an extending region along the first direction of the fluid passage defined by the first opening. The flow control valve according to claim 3 or 4, wherein the flow control valve is provided.   In a state where the valve body is in contact with the valve seat of the second opening, one end side of the second opening is opened close to the inner wall of the valve seat of the second opening. 6. The flow control valve according to claim 3, wherein the flow control valve is characterized in that A compressor,
An outdoor heat exchanger,
A pair of indoor heat exchangers;
A refrigerant circulation passage that sequentially passes through the compressor, the outdoor heat exchanger, and the pair of indoor heat exchangers;
The flow rate control valve according to any one of claims 6 to 12, wherein the flow rate control valve is incorporated in a circulation passage connecting the pair of indoor heat exchangers, and a first opening of the flow rate control valve is the outdoor heat exchanger. And the second opening is connected to the other indoor heat exchanger side following the compressor, and is connected to one indoor heat exchanger side.

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