JP5196983B2 - Flow control valve - Google Patents

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, a flow control valve 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, and a reverse contact with the valve seat portion. A valve rod having a valve body portion having a conical tapered surface, and in order to squeeze out the refrigerant even when the valve body portion abuts on the valve seat portion, the valve seat portion, A bleed groove having a predetermined depth is formed, and a plurality of recesses having a predetermined depth are arranged in parallel at the bottom of the bleed groove so as to distribute and lead out the refrigerant, and the tapered surface of the valve seat portion The angle α, which is a half of the angle obtained by subtracting the central angle θb of the tapered surface of the valve body portion from the central angle θa, is 1.0 ° or more and 2.5 ° or less.

In this case, in a preferred embodiment, the recess of the bottom is arranged in a predetermined depth of the bleed groove in cross section V-shaped, semi-elliptical shape, a recess having a predetermined depth of the trapezoidal shape or the like.

In the flow control valve according to the present invention, the angle α, which is a half of the angle 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 1.0 ° or more. 2.5 ° because it is less, between the tapered surface and the tapered surface of the valve seat portion of the valve body in cross section a gap Sa of like acute triangle formed upstream of their abutting portion, The angle α is greatly reduced as compared with the conventional case where the angle α is around 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.

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.

  The flow control valve 1 of the illustrated embodiment is used for 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 is hermetically 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 lower end outer peripheral side of the lower large-diameter portion 20A of the valve stem 20 is formed on the valve seat portion 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 portion 14 </ b> 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 FIG. 4 and FIG. 5, one half of the angle obtained by subtracting the central angle θb of the tapered surface 21a of the valve body 21A from the central angle θa of the tapered surface 14a of the valve seat portion 14A . The angle α is not less than 1.0 ° and not more than 2.5 °, and is upstream of the contact portion P 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 is significantly 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. 6 and 7, the sound pressure (dB) representing the noise level is taken on the vertical axis, and the angle α (= (θa−θb) / 2) and time (s) are taken on the horizontal axis, respectively. As shown in the experimental value, the sound pressure increases as the angle α increases, and the sound pressure exceeds the standard allowable limit value of 33.8 dB when the angle α exceeds 2 °. It can be seen that the noise reduction effect is greatest when the angle α exceeds 1.0 ° 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.

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 .

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

Claims (2)

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 closed.
At the bottom of the bleed groove, a plurality of rows of recesses having a predetermined depth are arranged in parallel so as to distribute and derive the refrigerant,
The angle α, which is a half of the angle 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 1.0 ° or more and 2.5 ° or less. A flow control valve characterized by comprising: 2. The flow rate according to claim 1, wherein the recesses having a predetermined depth arranged in parallel at the bottom of the bleed groove are recesses having a predetermined depth such as a V-shaped, semi-elliptical arc, or trapezoidal cross section. Control valve.

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