JP2009144893A - Flow rate control valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a flow rate control valve reducing as much as possible noise (refrigerant passing noise) generated by a refrigerant passing through a groove as a refrigerant delivering throttle portion. <P>SOLUTION: This flow rate control valve includes: a valve seat member 14 having a valve seat portion 14A formed with an inverted conical tapered surface 14a; and a valve rod 20 having a valve element portion 21A formed with an inverted conical tapered surface 21a approaching and separated with respect to the valve seat portion 14A. The valve seat portion 14A is provided with a bleed groove 17 of a predetermined depth in order to throttle and deliver the refrigerant even during a valve closing period when the valve element portion 21A abuts on the valve seat portion 14A. An angle α obtained by subtracting the center angle θb of the tapered surface 21a of the valve element portion 21A from the center angle θa of the tapered surface 14a of the valve seat portion 14A is 0°to 2.5°. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a solenoid (electromagnetic) drive type or motor drive type flow control valve used in an air conditioner or the like, and in particular, a refrigerant derivation in which a refrigerant is squeezed out even in a closed state in a valve seat portion. The present invention relates to a structure in which a bleed groove is formed as a throttle part.

  Conventionally, in a flow control valve used in an air conditioner or the like, as seen in, for example, the following Patent Documents 1 and 2, etc., a refrigerant derivation throttling portion (for example, when performing dehumidification (dry) operation) ( It is known that a valve seat portion (valve seat) is provided with a groove as a refrigerant to be squeezed out even in a closed state.

  However, as in the conventional flow rate control valve, simply providing a groove as the refrigerant outlet restricting portion in the valve seat portion causes unpleasant noise (refrigerant passing sound) due to the refrigerant passing through the groove. There was a problem.

  Therefore, in order to reduce such noise (refrigerant passing sound) as much as possible, the inventors of the present application have previously proposed a flow control valve as described in Patent Document 3 below.

  That is, the proposed flow control valve includes a valve seat member having a valve seat portion having an inverted conical tapered surface, and a valve body portion having an inverted conical tapered surface contacting and separating from the valve seat portion. The valve seat portion is formed with a bleed groove having a predetermined depth so that the refrigerant is squeezed out even when the valve body portion is in contact with the valve seat portion. A plurality of rows of concave portions having a predetermined depth such as a triangular shape, a semicircular arc shape, and a trapezoidal shape are arranged in parallel at the bottom portion of the bleed groove so that the refrigerant is distributed and led out.

  In the proposed control valve having such a configuration, at the time of dehumidification (dry) operation of the refrigerant air conditioner, the refrigerant is dispersed in the bleed groove and at the same time, is further dispersed in the concave portion. In addition, noise (refrigerant passing sound) due to the refrigerant passing through the bleed groove can be effectively reduced, and noise reduction can be achieved.

Japanese Patent Laid-Open No. 11-51514 JP 2004-150580 A Japanese Patent Application No. 2006-158785

  However, even in the proposed control valve, there is a strong demand for the development of a flow rate control valve that does not have a sufficient noise reduction effect and can achieve further noise reduction.

  The present invention has been made to meet the above-mentioned demands, and the object of the present invention is to reduce as much as possible noise (refrigerant passing sound) generated by the refrigerant passing through the bleed groove as the refrigerant outlet throttle part. Accordingly, it is an object of the present invention to provide a flow control valve that can achieve further noise reduction.

  In order to achieve the above object, one of the flow control valves according to the present invention basically includes a valve seat member having a valve seat portion having an inverted conical tapered surface, and a contact with the valve seat portion. A valve rod having a valve body portion having a tapered surface with an inverted conical surface that is separated from the valve seat, so that the refrigerant is squeezed out even when the valve body portion is closed against the valve seat portion. A bleed groove having a predetermined depth is formed in the portion, and an angle α obtained by subtracting the central angle θb of the tapered surface of the valve body portion from the central angle θa of the tapered surface of the valve seat portion is 0 ° or more. It is characterized by being 5 ° or less.

  In this case, in a preferred embodiment, a plurality of rows of recesses having a predetermined depth, such as a V shape, a semi-elliptical arc shape, and a trapezoidal shape, are arranged in parallel at the bottom of the bleed groove so that the refrigerant is distributed and led out. .

  In a more preferred embodiment, an angle α obtained by subtracting the central angle θb from the central angle θa is set to 1.0 ° or more and 1.5 ° or less.

  On the other hand, the other one of the flow control valves according to the present invention basically includes a valve seat member having a valve seat portion having a tapered surface with an inverted conical surface shape, and an inverted cone contacting and separating from the valve seat portion. A valve rod having a valve body portion having a planar tapered surface, and in order to squeeze and draw out the refrigerant even when the valve body portion is in contact with the valve seat portion, A bleed groove having a depth is formed, and on the upstream side of the taper surface in the valve body portion, a bulge portion is provided that bulges in the radial direction and whose lower surface faces the upper end surface of the valve seat portion, A separation distance β between the lower surface of the bulging portion and the upper end surface of the valve seat portion when the valve is closed is not more than a predetermined value.

  In this case, in a preferred embodiment, a plurality of rows of recesses having a predetermined depth, such as a V shape, a semi-elliptical arc shape, and a trapezoidal shape, are arranged in parallel at the bottom of the bleed groove so that the refrigerant is distributed and led out. .

  In another preferred embodiment, the upper end surface of the valve seat portion includes a plurality of rectifying grooves having a predetermined depth such as a V-shaped, semi-elliptical arc, or trapezoidal shape so as to cross the upper end surface in the radial direction. Provided.

The plurality of rectifying grooves are preferably arranged radially.
The plurality of rectifying grooves are preferably provided between adjacent bleed grooves.

  In one of the flow control valves according to the present invention, an angle α obtained by subtracting the central angle θb of the tapered surface of the valve body portion from the central angle θa of the tapered surface of the valve seat portion is 0 ° or more and 2.5 ° or less. Preferably, the cross section is formed between the taper surface of the valve body portion and the taper surface of the valve seat portion on the upstream side from the contact portion because it is 1.0 ° or more and 1.5 ° or less. However, the acute-angled triangular gap Sa is greatly reduced as compared with the conventional case where the angle α is about 8 °. For this reason, the bubbles contained in the passing refrigerant toward the bleed groove, which is a noise generation source, are sufficiently subdivided, and thereby noise (refrigerant passing sound) generated by the refrigerant passing through the bleed groove is reduced. It is possible to further reduce the noise and further silence.

  In another one of the flow control valves according to the present invention, a bulging portion is provided on the upstream side of the tapered surface in the valve body portion, and the lower surface of the bulging portion and the upper end surface of the valve seat portion when the valve is closed Is less than or equal to a predetermined value, relatively large (diameter) bubbles from the outer peripheral sides of the valve seat portion and the valve body portion toward the bleed groove are formed on the lower surface of the bulging portion and the valve seat portion. It becomes impossible to enter into the gap formed between the upper end surface of each other. For this reason, relatively large (diameter) bubbles contained in the passing refrigerant toward the bleed groove, which is a noise generation source, are subdivided, and thereby noise generated by the refrigerant passing through the bleed groove (refrigerant passing sound). Can be further reduced than before, and further noise reduction can be achieved.

  In this case, in addition to the above-described configuration, it is possible to further reduce the noise by providing a plurality of rectifying grooves in a predetermined form on the upper end surface of the valve seat portion to rectify the refrigerant.

Hereinafter, an embodiment of a flow control valve of the present invention will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing an embodiment of a flow control valve according to the present invention.

  A flow control valve 1 of the illustrated embodiment is used in a refrigeration cycle such as an air conditioner, and has a stepped can 12 comprising a reverse-bottomed cylindrical small-diameter portion 12A and a large-diameter portion 12B connected to the lower portion thereof. And a valve seat member 14 having a hook-like portion that is fitted into the large-diameter portion 12B of the can 12 from below and sealed and joined by welding or the like. The inner peripheral side of the upper end portion of the valve seat member 14 is a valve seat portion 14A having an inverted conical tapered surface 14a. The valve body 21A having a tapered surface 21a having an inverted conical surface is provided in contact with and away from the valve body (described later).

  A conduit (joint) 41 is joined to one side of the large-diameter portion 12B of the can 12, and a conduit (joint) 42 is joined and connected to the lower portion of the valve seat member 14 by brazing or the like. .

  A suction element 22, which is a fixed iron core, is fixed to the lower part of the small diameter part 12 </ b> A of the can 12 by brazing, caulking, or the like, and the suction element 22, the large diameter part 12 </ b> B of the can 12, and the valve seat member 14. A valve chamber 15 is defined, and a lower large diameter portion 20A of the valve rod 20 is positioned in the valve chamber 15.

  A small diameter portion 20B of the valve stem 20 is slidably inserted into a through hole provided in the suction element 22, and an upper end portion of the valve stem 20 is slidably inserted into the upper portion of the can 12. It is inserted into the hollow plunger 24 and fixed by caulking.

  A compression coil spring 25 is interposed between the plunger 24 and the suction element 22, and this compression coil spring 25 always pulls the plunger 24 away from the suction element 22, that is, the valve body portion 21 </ b> A is a valve seat portion. It is energized in the direction of pulling away from 14A (the valve opening direction).

  An electromagnetic actuator 30 having a housing 32, a coil 33, a bobbin 34 and the like is attached to the outer peripheral side of the can 20 (the small diameter portion 20B). A stopper 37 having a hemispherical convex portion is fixed to the upper portion of the housing 32 with a rivet 36 or the like, and a plurality of (for example, four) hemispherical convex portions of the stopper 37 are provided on the can 20 side. The electromagnetic actuator 30 is positioned and fixed with respect to the can 20 by fitting into any of the hemispherical recesses.

  Under such a configuration, when the coil 33 is not energized, the plunger 24 is in the upper end position by the urging force of the compression coil spring 25, and the valve body 21A of the valve stem 20 is the valve seat member. It is away from 14 valve seat parts 14A. Accordingly, the refrigerant can freely flow between the two conduits 41 and 42 via the valve chamber 15 (here, the flow is based on the flow of the conduit 41 → the conduit 42 as indicated by an arrow in the figure).

  When the coil 33 is energized, the attractor 22 and the plunger 24 are magnetized by the magnetic field generated from the coil 33. The magnetic force of the attractor 22 pulls the plunger 24 toward the attractor 22 against the urging force of the compression coil spring 25. As a result, the valve body 21A of the valve stem 20 comes into contact with the valve seat portion 14A to close the valve (position shown in FIG. 1).

  In addition to the above configuration, in the present embodiment, the refrigerant is squeezed out in the valve closing state and led out from the conduit 41 to the conduit 42, that is, for performing refrigerant dehumidification (dry) operation in the air conditioner. As shown in FIG. 2, as shown in FIG. 2, as shown in FIG. 2, a bleed groove having a depth of d as shown in FIG. 3 at a plurality of locations (for example, 8 locations at 45 ° intervals) of the valve seat 14 A 17 is formed, and a plurality of rows (for example, two rows) of recesses 18 having a semi-elliptical arc shape and a depth e, for example, are arranged in parallel at the bottom portion 17B of the bleed groove 17 from the valve chamber 15 toward the conduit 42. Has been.

  As described above, by arranging a plurality of rows (e.g., two rows) of recesses 18 having a depth e in the bleed groove 17 having a depth d, the refrigerant can be used in the dehumidification (dry) operation of the refrigerant air conditioner. At the same time as being dispersed by the eight bleed grooves 17, it is further dispersed by the two rows of recesses 18, so that noise (refrigerant passing sound) due to the refrigerant passing through the bleed grooves 17 is effectively obtained. Can be reduced.

  The cross-sectional shape of the concave portion 18 is not limited to a semi-elliptical arc shape as shown in FIG. 3, and the cross-sectional shape may be a V shape, a semi-arc shape, a trapezoidal shape, or a combination thereof. .

  In addition to this configuration, the following configuration is further added to the flow control valve 1 of the present embodiment.

  That is, as shown in FIGS. 4 and 5, the angle α obtained by subtracting the central angle θb of the tapered surface 21a of the valve body portion 21A from the central angle θa of the tapered surface 14a of the valve seat portion 14A is 0 ° or more. 2.5 ° or less, more preferably 1.0 ° or more and 1.5 ° or less, and the contact between the tapered surface 21a of the valve body portion 21A and the tapered surface 14a of the valve seat portion 14A. The gap Sa having a sharp triangular cross section formed on the upstream side of the portion P is greatly reduced as compared with the conventional case where the angle α is about 8 °. For this reason, the bubbles contained in the refrigerant passing through toward the bleed groove 17 which is a noise generation source are sufficiently subdivided, thereby generating noise (refrigerant passing sound) generated by the refrigerant passing through the bleed groove 17. This can be further reduced than the conventional one, and further noise reduction can be achieved.

  In order to verify this effect, a prototype experiment was conducted, and the results shown in FIGS. 6 and 7 were obtained. That is, in FIG. 6 and FIG. 7, the experimental values are shown with the sound pressure (dB) representing the noise level on the vertical axis and the angle α (= θa−θb) and time (s) on the horizontal axis. As described above, the sound pressure increases as the angle α increases, and when the angle α exceeds 2 °, the sound pressure exceeds 33.8 dB, which is a standard allowable limit value. It can be seen that the noise reduction effect is greatest when the angle α is 1.0 ° or more and 1.5 ° or less.

  FIG. 8 shows sound pressure (dB) indicating the noise level when the number of recesses 18 in the bleed groove 17 is 1, 2, 3, 4 (see FIG. 9),. As can be seen, the number of the concave portions 18 is suitably 2 to 4, and even if the number is 5 or more, the noise reduction effect is not so much obtained.

  FIG. 10 shows the lower large-diameter portion 20A ′ and the valve seat member 14 of the valve stem 20 of another embodiment. In the present embodiment, the angle α is set to about 8 °, which is the same as that in the prior art. However, the bleed groove 17 and the like have the same configuration as in the previous embodiment, and the following configuration is added thereto. That is, a bulging portion 23 is provided on the upstream side of the tapered surface 21a of the valve body portion 21A in the radial direction and its lower surface 23a faces the upper end surface 14b of the valve seat portion 14A. The separation distance β between the lower surface 23a of the bulging portion 23 and the upper end surface 14b of the valve seat portion 14A is set to a predetermined value or less.

  By doing so, relatively large (diameter) bubbles from the outer peripheral sides of the valve seat portion 14A and the valve body portion 21A toward the bleed groove 17 are formed on the lower surface 23a of the bulging portion 23 and the valve seat portion 14A. It becomes impossible to enter the gap (β) formed between the upper end surface 14b and the upper end surface 14b. For this reason, relatively large (diameter) bubbles contained in the passing refrigerant toward the bleed groove 17 which is a noise generating source are subdivided, and thereby noise generated by the refrigerant passing through the bleed groove 17 (refrigerant passage). Sound) can be further reduced as compared with the conventional one, and further noise reduction can be achieved.

  In order to verify such an effect, a prototype experiment was conducted, and the result shown in FIG. 11 was obtained. That is, in FIG. 11, the vertical axis represents the sound pressure (dB) representing the noise level, the horizontal axis represents time (s), and the separation distance β was set to 0.15 mm, 0.30 mm, and 0.45 mm. As shown in the experimental test values in this case, it can be seen that the sound pressure increases as the separation distance β increases.

  In this case, in addition to the above configuration, as shown in FIG. 12, the upper end surface 14b of the valve seat portion 14 has a V-shaped cross section (semi-elliptical arc shape) so as to cross the upper end surface 14b in the radial direction. A plurality of rectifying grooves 14c having a predetermined depth f (which may be trapezoidal or the like) are arranged in a radial pattern (a total of 16 rectifying grooves 14 in a set of two with a 45 ° interval and 8 places). Here, each rectifying groove 14c is provided between the adjacent bleed grooves 17-17.

  In this way, by providing a plurality of rectifying grooves in a predetermined form on the upper end surface of the valve seat portion to rectify the refrigerant, as shown in FIG. 13, further noise reduction can be achieved.

The longitudinal cross-sectional view which shows one Embodiment of the flow control valve which concerns on this invention. The perspective view of the valve seat member shown by FIG. The expanded sectional view which shows the bleed groove | channel formed in the valve seat part of the valve seat member shown by FIG. The expanded sectional view of the lower large diameter part of the valve stem and the upper part of a valve seat member in one Embodiment of this invention. The enlarged view of the X section of FIG. The graph provided for description of the effect of one Embodiment of this invention. The graph provided for description of the effect of one Embodiment of this invention. The graph which shows the sound pressure at the time of changing the number of the recessed parts in a bleed groove | channel in one Embodiment of this invention. The expanded sectional view which shows the case where the number of the recessed parts in a bleed groove | channel in one Embodiment of this invention is four. The expanded sectional view of the lower large diameter part of the valve stem and the upper part of a valve seat member in other embodiments of the present invention. The graph provided for description of the effect of other embodiment of this invention. The enlarged sectional view of the lower large diameter part of the valve stem and the upper part of a valve seat member in another embodiment of the present invention, and the perspective view of a valve seat valve mouth member. The graph with which it uses for description of the effect of another embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Flow control valve 10 Valve main body 14 Valve seat member 14A Valve seat part 14a Tapered surface 14b Upper end surface 14c Rectification groove 17 Bleed groove 17B Bottom part 18 Recess 20 Valve rod 21A Valve body part 21a Tapered surface 23 Swelling part

Claims (8)

  A valve seat member having a valve seat portion having an inverted conical tapered surface, and a valve rod having a valve body portion having an inverted conical tapered surface contacting and separating from the valve seat portion; A flow control valve in which a bleed groove having a predetermined depth is formed in the valve seat portion so that the refrigerant is squeezed out even when the valve body portion is in contact with the valve portion, and the valve seat portion The flow rate control valve is characterized in that an angle α obtained by subtracting the central angle θb of the tapered surface of the valve body portion from 0 ° to 2.5 ° is obtained from the central angle θa of the tapered surface.   A plurality of rows of recesses having a predetermined depth, such as a V shape, a semi-elliptical arc shape, and a trapezoidal shape, are arranged in parallel at the bottom of the bleed groove so as to distribute and lead out the refrigerant. Item 2. The flow control valve according to Item 1.   3. The flow rate control valve according to claim 1, wherein an angle α obtained by subtracting the center angle θb from the center angle θa is 1.0 ° or more and 1.5 ° or less.   A valve seat member having a valve seat portion having an inverted conical tapered surface, and a valve rod having a valve body portion having an inverted conical tapered surface contacting and separating from the valve seat portion; A flow control valve in which a bleed groove having a predetermined depth is formed in the valve seat portion so that the refrigerant is squeezed out even when the valve body portion is in contact with the valve portion, and the valve body portion A bulging portion is provided on the upstream side of the taper surface in the radial direction and a lower surface thereof is opposed to an upper end surface of the valve seat portion, and the lower surface of the bulging portion and the valve seat portion when the valve is closed A flow rate control valve characterized in that the separation distance β from the upper end surface of the gas flow is not more than a predetermined value.   A plurality of rows of recesses having a predetermined depth, such as a V shape, a semi-elliptical arc shape, and a trapezoidal shape, are arranged in parallel at the bottom of the bleed groove so as to distribute and lead out the refrigerant. Item 5. The flow control valve according to Item 4.   A plurality of rectifying grooves having a predetermined depth such as a V shape, a semi-elliptical arc shape, and a trapezoidal shape are provided on the upper end surface of the valve seat portion so as to cross the upper end surface in the radial direction. The flow control valve according to claim 4 or 5, characterized in that   The flow control valve according to claim 6, wherein the plurality of rectifying grooves are arranged radially.   The flow control valve according to claim 6 or 7, wherein the plurality of rectifying grooves are provided between the adjacent bleed grooves.

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