JP4769036B2 - Throttle device, flow control valve, and air conditioner incorporating the same - Google Patents

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 through a space, and noise generated when passing through the orifice is buffered in the space to make it quiet.

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.

(Object of invention)
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.

First embodiment of the present invention includes a first member, a second member is superimposed on the first member, the gap portion that will be formed between the second member and the first member And a passage formed in the first member so that one end is open at the center side of the gap , and the second member or between the first member and the second member And a port having one end communicating only with an outer peripheral portion of the gap, the passage is arranged in an axisymmetric manner, and the gap extends in a direction intersecting the axis of the passage, In the throttling device, the gap portion defines a fluid passage along a radial direction with respect to the symmetry axis of the passage.

  In the present invention, when the fluid is introduced from the port to the outer peripheral portion of the gap, the fluid is guided to the passage that opens to the center thereof, and the fluid flows out from the other end of the passage. Conversely, when fluid is introduced from the other end of the passage, the fluid flows through the passage from the center side of the gap portion to a port communicating with the outer peripheral portion. In any case, an increase in fluid flow velocity and a decrease in pressure occur due to the throttling effect when passing through the passage. In particular, when the fluid is introduced from the port to the outer peripheral portion of the gap, the flow velocity of the fluid flowing in the gap toward the passage and the pressure gradually decrease. On the other hand, when the fluid is introduced from the other end of the passage, the flow velocity of the fluid gradually decreases immediately after passing through the passage, and stabilization of the reduced pressure occurs in the gap.

  In the throttling device according to the first aspect of the present invention, it is preferable that the interval between the gaps along the axis of the passage is set smaller than the inner diameter of the passage.

According to a second aspect of the present invention, the first member, the second and third members that are overlapped with each other with the first member interposed therebetween, the second and third members, and the first member Between the first member and the second member, and the second and third members, or between the first member and the second and third members. And a first port and a second port , one end of which communicates only with the outer peripheral portions of the first and second gaps, respectively, and the passage is arranged symmetrically with respect to the first and second ports . In the throttling device, the gap extends in a direction intersecting the axis of the passage .

  In the present invention, when the fluid is introduced from the first port to the outer peripheral portion of the first gap portion, the fluid is guided to the passage opened to the center side, and the second gap portion is passed through this passage. The fluid flows from the center side to the second port communicating with the outer periphery thereof. On the contrary, when the fluid is introduced from the second port to the outer peripheral portion of the second gap, the fluid is guided to the passage opening to the center side, and the center of the first gap is passed through this passage. Fluid flows from the side to the first port communicating with the outer periphery. In any case, an increase in fluid flow velocity and a decrease in pressure occur due to the throttling effect when passing through the passage. When the fluid is introduced from the first port to the outer peripheral portion of the first gap, the flow velocity of the fluid gradually decreases immediately after passing through the passage, and the stabilized pressure is reduced in the second gap. Happens. Similarly, when a fluid is introduced from the second port to the outer peripheral portion of the second gap, the flow rate of the fluid gradually decreases immediately after passing through the passage, and the stabilized pressure is reduced in the first gap. Will happen.

  In the expansion device according to the second aspect of the present invention, it is preferable that the interval between the first gap portions along the axis of the passage is set smaller than the inner diameter of the passage. Similarly, it is preferable that the interval between the second gaps along the axis of the passage is set smaller than the inner diameter of the passage.

  The first cavity may define a fluid passage along a radial direction with respect to the symmetry axis of the passage. The second cavity can likewise define a fluid passage along the radial direction with respect to the symmetry axis of the passage.

According to a third 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 to drive the valve body in the second direction. The valve body includes a first member, second and third members that are overlapped with each other with the first member interposed therebetween, and the second and third members and the first member. each first and second void portion Ru is formed, both ends respectively to the center side of the first and second gap portions between the A throttle passage formed in the first member so that the mouth, the one second member, or is formed between the first member and the second member, one end of the first gap Between the first port and the third member, or between the first member and the third member. The first port communicates only with the outer peripheral portion of the portion and the other end communicates with the valve chamber of the valve housing. is formed, it has a second port to which the other end is opposed to said second opening with one end communicated with only the outer peripheral portion of the second cavity portion, wherein the throttle passage and said second direction The first and second gap portions are arranged symmetrically with respect to parallel axes and extend in a direction intersecting with the axis of the passage .

  In the present invention, when the valve body is separated from the valve seat of the second opening by the driving means and the second opening is opened, the first opening and the second opening are the valve housing. It is in a communicating state through the valve chamber. Therefore, the fluid flows freely between the first opening and the second opening regardless of the presence or absence of the throttle passage incorporated in the valve body.

  On the other hand, in a state where the valve body is in contact with the valve seat of the second opening by the driving means and the second opening is closed, the first port passes through the first opening to the first port. When the fluid is introduced to the outer peripheral portion of the gap, the fluid is guided to the throttle passage that opens to the center side, and the second communication portion communicates with the outer periphery from the center side of the second gap portion through the passage. The fluid flows through the two ports to the second opening. On the contrary, when the fluid is introduced from the second port to the outer peripheral portion of the second gap through the second opening, the fluid is guided to the throttle passage that opens to the center side. The fluid flows through the first opening through the passage and through the first port communicating with the outer periphery from the center of the first gap. In any case, the first opening and the second opening are in communication with each other through the throttle passage, and the fluid flow rate increases and the pressure decreases due to the throttle effect when passing through the throttle passage. . When the fluid is introduced from the first port to the outer periphery of the first gap, the flow rate of the fluid immediately after passing through the throttle passage gradually decreases and the pressure is stabilized in the second gap. Occur. Similarly, when the fluid is introduced from the second port to the outer peripheral portion of the second gap, the flow velocity of the fluid immediately after passing through the throttle passage gradually decreases and the pressure stabilization is performed in the first gap. Will happen.

  In the flow control valve according to the third aspect of the present invention, when the valve body is in contact with the valve seat of the second opening, the first port is a fluid passage defined by the first opening. It is preferably located in the extending region along the first direction.

  The valve body may have a plurality of first ports, and may further include an annular rectifying member surrounding the first ports.

  The first cavity may define a fluid passage along a radial direction with respect to the axis of symmetry of the throttle passage. The second cavity can likewise define a fluid passage along the radial direction with respect to the axis of symmetry of the throttle passage.

  It is preferable to set the interval between the first gap portions along the second direction to be smaller than the inner diameter of the throttle passage. Similarly, it is preferable to set the interval between the second gap portions along the second direction to be smaller than the inner diameter of the throttle passage.

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

  According to a fourth aspect of the present invention, 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 And a flow control valve according to the third embodiment of the present invention incorporated in a circulation passage connecting the pair of indoor heat exchangers, and a first opening of the flow control valve is connected 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 according to the first embodiment of the present invention, when obtained by introduction of the fluid from the other end of the through passage, increase will occur and the pressure drop of the flow velocity of the fluid by the diaphragm effect when passing through the passage, further the passage The flow rate of the fluid immediately after passing through gradually decreases and pressure stabilization occurs in the gap. As a result, even in the case of using a particularly easily vaporized fluid, an expansion sound accompanying vaporization does not occur instantaneously immediately after passing through the passage, and the inside of the gap after passing through the passage is sequentially generated during the flow. It can be made quieter than. Conversely, when fluid is introduced from the port, it can be guided into the passage while gradually decreasing the pressure while gradually increasing the flow velocity of the fluid in the gap.

According to the throttle device according to the second embodiment of the present invention, Ri increase and decrease in the pressure of the flow velocity of the fluid by the diaphragm effect of passing through the through path to put, in any case, the fluid immediately after passing through the passage flow rate Gradually decreases and pressure stabilization occurs in the gap. As a result, even in the case of using a particularly easily vaporized fluid, an expansion sound accompanying vaporization does not occur instantaneously immediately after passing through the passage, and the inside of the gap after passing through the passage is sequentially generated during the flow. It can be made quieter than. 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 interval between the first gap portions along the axis of the passage is set smaller than the inner diameter of the passage, when the fluid flows into the passage from the first gap portion, the bubbles contained in the fluid are less than the inner diameter of the passage. It is possible to subdivide, and it is possible to reduce the width of the pressure fluctuation generated when the bubbles pass through the passage. Conversely, when the fluid flows into the first gap through the passage, the pressure can be stabilized while further decreasing the flow velocity of the fluid that has been raised by the throttling effect in the passage.

  Similarly, when the interval between the second gap portions along the axis of the passage is set smaller than the inner diameter of the passage, the throttling effect in the passage when the fluid flows into the second gap portion through the passage. The pressure can be stabilized while further decreasing the flow rate of the fluid that has been raised by the above. On the contrary, when the fluid flows into the passage from the second gap portion, the bubbles included 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 passage. Can be reduced.

  If the first gap defines a fluid passage along the radial direction with respect to the symmetry axis of the passage, the size of the throttling device in the direction along the symmetry axis of the passage can be reduced.

  If the second gap defines a fluid passage along the radial direction with respect to the symmetry axis of the passage, the size of the throttle device in the direction along the symmetry axis of the passage can be further reduced.

According to the flow control valve of the present invention, a state where the communication with the first opening and the second opening without passing through the aperture Ri passage through a throttle passage first opening and the second opening It is possible to switch to a state where the part is in communication. Further, when the first and second openings are communicated via the throttle passage, the flow velocity of the fluid increases and the pressure decreases when passing through the throttle passage. As the flow rate of the gas gradually decreases, pressure stabilization occurs in the gap. As a result, even when using a fluid that is particularly easy to vaporize, the expansion sound that accompanies vaporization does not occur instantaneously immediately after passing through the passage, and the inside of the gap after passing through the passage is sequentially generated during the flow. Therefore, the noise can be reduced without using an expensive porous member. 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.

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

  In the case where the valve body has a plurality of ports and further includes an annular rectifying member surrounding the first ports, each of the first first ports particularly when fluid flows from the first opening side to the first ports. Even if the ports have different distances from the first opening, the flow rate of the fluid passing through the first ports can be made uniform.

  When the first gap portion defines a fluid passage along the radial direction with respect to the axis of symmetry of the throttle passage, the size of the valve body along the second direction can be reduced.

  Similarly, when the second gap portion defines a fluid passage along the radial direction with respect to the axis of symmetry of the throttle passage, the size of the valve body along the second direction can be further reduced.

  When the interval between the first gaps along the second direction is set smaller than the inner diameter of the throttle passage, when the fluid flows into the passage from the first gap, bubbles contained in the fluid are removed from the throttle passage. It is possible to subdivide the inner diameter, and 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 first gap through the throttle passage, the flow velocity of the fluid raised by the throttle passage can be lowered more slowly and the reduced pressure can be stabilized.

  Similarly, when the interval between the second gaps along the second direction is set to be smaller than the inner diameter of the throttle passage, when the fluid flows into the second gap through the throttle passage, The flow rate of the increased fluid can be reduced more slowly and the reduced pressure can be stabilized. On the contrary, when the fluid flows into the passage from the second gap, the bubbles included in the fluid can be subdivided from the inner diameter of the throttle passage, and the pressure fluctuation generated when the bubbles pass through the throttle passage It is possible to reduce the width of the.

  In a state where the valve body is in contact with the valve seat of the second opening portion, when the second port opens close to the inner wall of the valve seat of the second opening portion, the fluid flows from the second port. When flowing out to the second opening side, the fluid can flow along the inner wall of the valve seat of the second opening, and is easily separated into two phases of liquid on the inner peripheral side and gas on the outer peripheral side. Fluid mixing 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 third 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 11, 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 integrally caulked to the bottom of the plunger 39, the valve rod 41 is formed with the valve portion 35 at the tip, and the base side of the valve portion 35 is inserted from the base end side of the valve rod 41. A cylindrical rectifying member 42 that is tightly fitted to the valve body, a concave portion 43 that is formed in the valve portion 35 of the valve rod 41 and opens toward the second opening portion 29, and a diaphragm plate that is accommodated in the concave portion 43. 44 and a port plate 45. The diaphragm plate 44 and the port plate 45 obtained from metal or resin are the tip of the valve portion 35 of the valve stem 41 whose outer periphery is tapered toward the second opening 29 side, that is, the recess 43. By caulking the open end toward the inner peripheral side, it is held in the recess 43.

A diaphragm passage 46 extending in parallel with the second direction is formed in the center of the diaphragm plate 44 as the first member of the present invention. The diaphragm device is configured. A first gap extending between the throttle plate 44 and the bottom surface of the recess 43 extends in a direction intersecting the axis of the throttle passage 46, in the present embodiment, in a direction substantially perpendicular to the second direction. A portion 47 is formed . A direction intersecting the axis of the throttle passage 46 between the throttle plate 44 and the port plate 45 as the second member of the present invention , in the present embodiment, a direction substantially perpendicular to the second direction. A second gap 48 extending in the direction is formed. Accordingly, the valve stem 41 also functions as the third member of the present invention, and the distance along the second direction between the first and second gap portions 47 and 48 (the height in the vertical direction in FIG. 3). Are set narrower than the inner diameter of the throttle passage 46. In general, it is generally preferable to set these intervals as narrow as about 1/4 of the inner diameter of the throttle passage 46, because the reason is that between the throttle passage 46 and the first and second gap portions 47 and 48. This is because the change in the cross-sectional area of the channel becomes the smoothest. From the viewpoint of noise reduction, it can be said that it is preferable to set these intervals as narrow as possible. The two gaps 47, 48 communicating with both sides of the throttle passage 46 define a slit-like refrigerant passage extending in a direction orthogonal to the axis of the throttle passage 46, and therefore noise generated in the throttle passage 46. However, it is difficult for the two gaps 47 and 48 to be transmitted from the outer peripheral side to the outer side, and good silentness can be obtained.

  In the present embodiment, a step portion 49 is formed on the inner wall of the concave portion 43, and the first gap portion 47 is formed by locking the diaphragm plate 44 to the step portion 49. In addition, the second gap 48 is formed by forming a recess 50 on the end face of the aperture plate 44 facing the port plate 45 except for the outer peripheral edge portion thereof, but the aperture plate 44 and the port plate 45 It is also possible to form the second gap 48 having an interval corresponding to the thickness of the spacer by interposing an annular spacer therebetween.

  A plurality of first ports 51 whose one end opens to the outer peripheral surface of the valve stem 41 and whose other end opens to the inner peripheral portion of the recess 43 are formed radially at the base of the valve portion 35 of the valve stem 41. The 1 port 51 communicates the outer peripheral portion of the first gap portion 47 and the valve chamber 25 of the valve housing 26. Accordingly, the first gap 47 defines a fluid passage along the radial direction with respect to the axis of the throttle passage 46. As described above, in the present embodiment, a plurality of the first ports 51 are formed radially with respect to the axis of the valve stem 41, but a larger amount of refrigerant can be supplied to and discharged from the outer peripheral portion of the first gap portion 47. The first gap 51 is opened so that the first port 51 opens in an arc shape extending along the circumferential direction of the valve rod 41, or the refrigerant forms a swirling flow in the first gap 47. It is also possible to form a plurality of first ports 51 in a direction extending in a tangential direction with respect to the inner wall.

  The rectifying member 42 described above is disposed so as to surround the opening end on the outer peripheral side of the first port 51 with an annular gap therebetween, and the first rectifying member 42 is interposed through the gap formed between the valve rod 41 and the rectifying member 42. The 1 port 51 and the valve chamber 25 of the valve housing 26 communicate with each other. By surrounding the opening end on the outer peripheral side of the first port 51 with the rectifying member 42, the refrigerant inflow / outflow state in all the first ports 51 is made uniform regardless of the distance from the first opening portion 27. It becomes possible. Further, since the noise generated in the throttle passage 46 and transmitted to the first port 51 is blocked by the rectifying member 42, the noise is reduced.

  Further, in the present embodiment, the outer peripheral side of the first port 51 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. Is 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 51 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.

  In the port plate 45, a plurality of second ports 52 communicating with the outer peripheral portion of the second gap portion 48 and facing the second opening 29 are formed annularly at predetermined intervals along the circumferential direction. The second cavity 48 defines a fluid passage along a radial direction with respect to the axis of the throttle passage 46. The second ports 52 can also be formed by arc-shaped elongated holes extending in the circumferential direction.

  The driving means 31 of the valve body 30 in the present embodiment uses an electromagnetic coil 53, and a bobbin 54 that houses the electromagnetic coil 53, and the bobbin 54 is embedded together with the electromagnetic coil 53 via a sealing resin 55. And a frame-like casing 57 fixed to the plug 38 via a bolt 56. A cable 58 drawn out from the electromagnetic coil 53 via the sealing resin 55 is connected to a power source via an ON / OFF circuit (not shown). The bobbin 54 is disposed so as to surround the plunger 39 via the guide tube 34, and generates an electromagnetic force that moves the plunger 39 toward the valve housing 26 when energized.

  A compression coil spring 59 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 53 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 59, and the valve portion 35 is moved to the valve seat 28. Is brought into a closed state as shown in FIG. As a result, the gas-liquid two-phase refrigerant flowing into the valve chamber 25 of the valve housing 26 from the first opening 27 passes through the first port 51 from the gap between the valve rod 41 and the rectifying member 42. Of the air gap 47 is gradually compressed as it advances radially inward from there, and large bubbles are subdivided and flow into the central throttle passage 46, where they are further compressed and subjected to a predetermined flow rate. The refrigerant is guided to the second opening 29 side. The refrigerant guided from the throttle passage 46 to the second gap 48 radially expands radially outward, but since the interval between the second gaps 48 is narrow, the rapid expansion is suppressed and the refrigerant expands gently. Then, it flows out from the second port 52 to the second opening 29. 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 the refrigerant. In the embodiment, since the opening end of the second port 52 facing the second opening 29 is open close to the inner wall of the second opening 29, the second port 52 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. From such a viewpoint, it is also effective to incline the second port 52 toward the inner wall of the second opening 29.

  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.

  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 46 formed in the throttle plate 44, 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.

  The cross-sectional structure of the main part of another embodiment of the flow control valve according to the present invention based on such a viewpoint is shown in FIG. 5 and the appearance of the port plate is shown in an enlarged view in FIG. The same reference numerals are used for functional elements, and duplicate descriptions are omitted. That is, the first port 51 in the present embodiment is formed so as to open to the base end surface of the valve portion 35 and the outer peripheral portion of the first gap portion 47, and is made of metal so as to contact the base end surface of the valve portion 35. A cylindrical filter 60 formed of a mesh is fitted on the base side of the valve portion 35 of the valve rod 41. The other end surface of the filter 60 is integrally fixed to the valve portion 35 by a caulking portion 61 formed on the outer periphery of the valve rod 41 so that the one end surface side of the filter 60 completely covers the first port 51. In the present embodiment, a presser ring 62 is interposed between the caulking portion 61 and the other end surface of the filter 60 so that the other end surface of the filter 60 is not damaged by the caulking portion 61. Further, the port plate 45 in the present embodiment is formed by notching a part of the outer peripheral edge so that the second port 52 is formed between the inner periphery of the recess 43 and the notch 63. Forms a second port 52 between the inner periphery of the recess 43. From this point of view, the port plate 45 can be polygonal or gear-shaped.

  Therefore, the refrigerant guided from the first opening 27 to the first port 51 via the filter 60 is trapped by the filter 60 while passing through the filter 60 and prevents the foreign substance from flowing into the throttle passage 46 side. be able to. In this embodiment, the opening end of the second port 52 facing the second opening 29 can be made closer to the inner wall side of the second opening 29 than in the previous embodiment. Air bubbles adhering to the inner wall can flow more reliably.

  In the two embodiments described above, the throttle plate 44 and the port plate 45 are fixed to the recess 43 by caulking the tip of the valve portion 35, but the valve portion 35 is made independent from the valve rod 41, and this is connected to the port plate 45. It is also possible to function as.

  FIG. 7 shows the cross-sectional structure of the main part of still another embodiment of the flow control valve according to the present invention based on such a viewpoint, FIG. 8 shows the external appearance of the tip of the valve body 30, and FIG. However, elements having the same functions as those of the previous embodiment are designated by the same reference numerals, and redundant descriptions are omitted. That is, a flange portion 64 provided with a plurality of first ports 51 is formed at the tip of the valve stem 41 in the present embodiment. The valve member 65 whose proximal end is caulked to the outer peripheral edge of the flange portion 64 is formed with a recess 43 for accommodating the throttle plate 44, and the recess plate 43 and the distal end surface of the valve rod 41 are formed by the recess 43. A first gap 47 is formed between the two. A receiving plate portion 66 is formed on the distal end surface side of the valve member 65 facing the second opening 29 so as to cross the recess 50 of the throttle plate 44. The receiving plate portion 66 is opposed to the distal end side of the concave portion 43 of the valve member 65 with an angle of 180 degrees about the axis of the valve stem 41, and each has an arcuate opening, and the diaphragm plate 44 facing this opening portion. The recess 50 functions as a pair of second ports 52.

  By separating the valve rod 41 and the valve member 65, the outer peripheral portion of the valve member 65 facing the second opening 29 can be finished more smoothly. For this reason, it becomes possible to control more accurately the direction of the refrigerant flowing out from the second port 52 to the second opening 29 side, and the bubbles attached to the inner wall of the second opening 29 are more efficiently separated. be able to.

  In the embodiment described above, one throttle passage 46 is formed in the center of the throttle plate 44 coaxially with the axis of the valve stem 41, but a plurality of throttle passages 46 are formed symmetrically with respect to the axis of the second opening 29. It is also possible. FIGS. 10 and 11 show the cross-sectional structures of the main parts 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.

  The embodiment shown in FIG. 10 has a plurality of throttle passages 46 with the axis of the valve stem 41 as an axis of symmetry, and these throttle passages 46 are formed on the base end surface of the valve portion 35 at the distal end portion of the valve stem 41. It opens to the outer peripheral side and the bottom center of the recess 43 of the valve portion 35. A port plate 45 is fixed to the recess 43 so as to form the second gap 48 between the bottom surface and the inner wall of the second plate 52. The valve rod 41 between the plunger 39 and the valve portion 35 is formed with a first gap portion 47 between the base end surface of the valve portion 35 and the filter 60 between the outer peripheral edge portion of the valve portion 35. A cylindrical spacer 67 for clamping is fitted.

  In the present embodiment, the base end surface of the valve portion 35 is inclined in a conical shape so that the refrigerant passage length along the radial direction can be as long as possible. It is also possible to set the angle perpendicular to the axis of the opening 29.

  Further, in the present embodiment, the previous valve housing 26 is formed by pressing a sheet metal such as stainless steel, and a housing main body 68 integrated with the guide tube 34 and a second opening 29 having a valve seat 28 are formed. An annular receiving plate 70 for locking the collar 36 is fixed to the housing main body 68 in a state where it is caulked. In this case, the housing main body 68 and the valve seat block 69 are integrally joined together with the first and second pipe joints 32 and 33 by brazing in a furnace in a hydrogen atmosphere, for example. Reference numeral 71 denotes each. In the present embodiment, since the first pipe joint 32 functions as the first opening, it is not necessary to form the first opening in the housing body 68.

  Accordingly, the refrigerant that passes through the filter 60 from the first pipe joint 32 in the valve-closed state has an annular shape on the outer periphery of the first gap portion 47 formed between the base end surface of the valve portion 35 and the spacer 67. The gas is guided from the first port 51 to the throttle passage 46 and flows out from the second port 52 to the second opening 29 side through the second gap 48.

  On the other hand, in the embodiment shown in FIG. 11, the port plate 45 is formed in an annular shape, and is fitted into a shaft portion 72 protruding from the bottom surface of the valve portion 35 to be caulked integrally. In the present embodiment, an annular second port 52 is formed between the inner wall of the recess 43 and the outer peripheral surface of the port plate 45, and the annular second port 52 faces the inner wall of the second opening 29. By opening, the refrigerant flowing out from here blows out toward the inner wall of the second opening 29, and the bubbles attached to the second opening 29 can be more efficiently separated. . The second gap 48 is formed between the bottom surface of the recess 43 and the port plate 45, and a plurality of throttle passages 46 are opened at the bottom of the valve portion 35.

  Also in the present embodiment, the refrigerant flows radially inward in the first gap 47, passes through the throttle passage 46, then flows again radially outward in the second gap 48, and finally the second gap. The fluid flows out from the port 52 along the inner wall of the second opening 29. Needless to say, the filter 60 contributes to the rectifying 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. FIG. 6 is a three-dimensional projection view illustrating an enlarged appearance of a port plate in the flow control valve illustrated in FIG. 5. It is sectional drawing showing the schematic structure of other embodiment of the flow control valve by this invention. It is a three-dimensional projection figure showing the external appearance of the front-end | tip part of the valve body in embodiment shown in FIG. It is a front view of the front-end | tip part of the valve body shown in FIG. It is sectional drawing showing the schematic structure of another embodiment of the flow control valve by this invention. It is sectional drawing showing the schematic structure of another 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 Rectifying member 43 Concave 44 Diaphragm plate 45 Port plate 46 Constriction passage 47 First gap 48 Second gap 49 Step 50 Depression 51 First port 52 Second port 53 Electromagnetic coil 54 Bobbin 55 Sealing resin 56 Bolt 57 Casing 58 Cable 59 Compression coil spring 60 Filter 61 Caulking portion 62 Presser ring 63 Notch 64 Flange portion 65 Valve member 66 Receiving plate portion 67 Spacer 68 Housing body 69 Valve seat block 70 Receiving plate 71 Brazing portion 72 Shaft portion Z Along the first direction of the refrigerant passage defined by the first opening portion Extension area

Claims (16)

A first member;
A second member superimposed on the first member;
A gap portion that will be formed between the second member and the first member,
A passage formed in the first member so that one end is open on the center side of the gap,
The second member, or a port formed between the first member and the second member and having one end communicating with only the outer peripheral portion of the gap, and the passage is arranged symmetrically. And the gap extends in a direction intersecting the axis of the passage, the gap defining a fluid passage along a radial direction with respect to the symmetry axis of the passage. apparatus.   The aperture device according to claim 1, wherein an interval between the gaps along the axis of the passage is set smaller than an inner diameter of the passage. A first member;
A second member and a third member which are superposed on each other with the first member interposed therebetween;
First and second gaps formed between the second and third members and the first member, respectively;
A passage formed in the first member such that both ends open to the center side of the first and second gaps, and
Formed between the second and third members or between the first member and the second and third members, one end communicating only with the outer peripheral portion of the first and second gaps, respectively . A first port and a second port , wherein the passage is axially symmetrical and the first and second gaps extend in a direction intersecting the axis of the passage. Characteristic diaphragm device. Spacing of the first gap portion along the axis of the passage, the diaphragm device according to claim 3, characterized in that it is set smaller than the inner diameter of the passageway.   5. The aperture device according to claim 3, wherein an interval between the second gaps along the axis of the passage is set smaller than an inner diameter of the passage.   The throttling device according to any one of claims 3 to 5, wherein the first gap portion defines a fluid passage along a radial direction with respect to an axis of symmetry of the passage.   The throttling device according to any one of claims 3 to 6, wherein the second gap portion defines a fluid passage along a radial direction with respect to an axis of symmetry of the 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 so as to intersect 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 movably held in the second direction, and driving means connected to the valve housing to drive the valve body in the second direction,
A first member;
A second member and a third member which are superposed on each other with the first member interposed therebetween;
A first and second void portion Ru respectively formed between the second and third member and said first member,
A throttle passage formed in the first member such that both ends thereof are open to the center side of the first and second gaps, and
The second member or the first member is formed between the first member and the second member, and one end communicates only with the outer peripheral portion of the first gap and the other end is the valve of the valve housing. a first port communicating with the chamber,
The third member or the first member is formed between the first member and the third member, and one end communicates only with the outer periphery of the second gap and the other end is the second opening. have a second port that faces the part, relative to the first and second axis of the gap portion is the passage together with the throttle passage is arranged symmetrically with respect to said second direction parallel to the axis A flow control valve characterized by extending in a crossing direction .   In a state where the valve body is in contact with the valve seat of the second opening, the first port extends along the first direction of the fluid passage defined by the first opening. The flow control valve according to claim 8, wherein the flow control valve is located in a region.   10. The flow control valve according to claim 8, wherein the valve body includes a plurality of the first ports and further includes an annular rectifying member surrounding the first ports. 11.   11. The flow control valve according to claim 8, wherein the first gap portion defines a fluid passage along a radial direction with respect to an axis of symmetry of the throttle passage. .   The flow control valve according to any one of claims 8 to 11, wherein the second gap portion defines a fluid passage along a radial direction with respect to an axis of symmetry of the throttle passage. .   The flow control valve according to any one of claims 8 to 12, wherein an interval between the first gap portions along the second direction is set smaller than an inner diameter of the throttle passage. .   The flow control valve according to any one of claims 8 to 13, wherein an interval between the second gap portions along the second direction 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 second port opens close to the inner wall of the valve seat of the second opening. The flow control valve according to any one of claims 8 to 14. 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 8 to 15, wherein the flow rate control valve is incorporated in a circulation passage connecting the pair of indoor heat exchangers, and the 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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